CN111472978A - Flow guide pipe structure, fixed scroll part, compressor assembly and compressor system - Google Patents
Flow guide pipe structure, fixed scroll part, compressor assembly and compressor system Download PDFInfo
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- CN111472978A CN111472978A CN201910066927.8A CN201910066927A CN111472978A CN 111472978 A CN111472978 A CN 111472978A CN 201910066927 A CN201910066927 A CN 201910066927A CN 111472978 A CN111472978 A CN 111472978A
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- vapor injection
- enhanced vapor
- compressor
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- vanes
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- 238000002347 injection Methods 0.000 claims abstract description 117
- 239000007924 injection Substances 0.000 claims abstract description 117
- 239000012530 fluid Substances 0.000 claims abstract description 61
- 230000005540 biological transmission Effects 0.000 claims abstract description 3
- 230000001154 acute effect Effects 0.000 claims description 7
- 238000007599 discharging Methods 0.000 claims 1
- 238000007906 compression Methods 0.000 description 13
- 230000006835 compression Effects 0.000 description 11
- 230000007246 mechanism Effects 0.000 description 8
- 230000010349 pulsation Effects 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 238000004891 communication Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 230000001502 supplementing effect Effects 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
- 230000000153 supplemental effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/122—Arrangements for supercharging the working space
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Rotary Pumps (AREA)
Abstract
The invention provides a flow guide tube structure for a compressor assembly with enhanced vapor injection, the compressor assembly comprising a compressor, an enhanced vapor injection fluid source and an enhanced vapor injection pipeline adapted to supply enhanced vapor injection fluid from the enhanced vapor injection fluid source to a medium pressure chamber of the compressor, the flow guide tube structure comprising a flow guide tube disposed in the enhanced vapor injection pipeline to form at least a portion of a flow path for the enhanced vapor injection fluid, wherein the flow guide tube comprises: an inlet positioned on a side of the enhanced vapor injection fluid source to receive enhanced vapor injection fluid and an outlet positioned on a side of the intermediate pressure chamber to discharge the received enhanced vapor injection fluid; a tube wall; and a vane formed to extend obliquely from an inner wall surface of the pipe wall toward the outlet to suppress outward transmission of the pressure pulse in the intermediate-pressure chamber.
Description
Technical Field
The present invention relates to a draft tube structure, and more particularly, to a draft tube structure for a compressor assembly having enhanced vapor injection. The present invention also relates to a non-orbiting scroll member, and more particularly, to a non-orbiting scroll member having a nozzle structure. The invention also relates to a compressor assembly with the flow guide pipe structure and a compressor system.
Background
Existing compressor systems for cooling/heating (including air conditioners, refrigeration equipment, etc.) generally include a compressor, a condenser, a main throttle device, and an evaporator, which are connected in sequence to form a circulation circuit. In the low-temperature heating working condition, in order to increase the heating quantity, a method of increasing enthalpy by injection is adopted in the prior art. The enhanced vapor injection line typically includes an economizer with a throttle device connected to the intermediate pressure gas port of the compressor to supplement the intermediate pressure cavity of the compressor with enhanced vapor injection fluid to increase the compressor discharge and thereby increase the amount of heat produced at low temperatures. Similarly, supplemental enhanced vapor injection fluid (make-up air) may also be used to increase the capacity of the compressor system.
However, during the operation of the enhanced vapor injection compressor, since the enhanced vapor injection pipeline is directly connected to the middle pressure part of the compressor, such as the scroll chamber of the scroll compressor or the compression chamber of the gear compressor, and the pressure in the middle pressure chamber fluctuates along with the movement of the compression part, the pressure fluctuation can cause the vibration and noise of the enhanced vapor injection pipeline and can cause the impact on the valve piece on the enhanced vapor injection pipeline.
Therefore, there is a need for improvements in enhanced vapor injection piping to reduce vibration and noise in the piping and to reduce the impact on the valve components.
Disclosure of Invention
It is an object of the present invention to solve or at least mitigate at least one of the above problems by providing a device that reduces or even eliminates the reverse flow of fluid in the enhanced vapor injection path, thereby reducing vibration and noise of the pipeline and avoiding damage to the valve body in the path.
According to one aspect of the present invention, there is provided a flow conduit structure for a compressor assembly having enhanced vapor injection, the compressor assembly comprising a compressor, a source of enhanced vapor injection fluid, and an enhanced vapor injection conduit adapted to supply enhanced vapor injection fluid from the source to a medium pressure chamber of the compressor, the flow conduit structure comprising a flow conduit disposed in the enhanced vapor injection conduit to define at least a portion of a flow path for the enhanced vapor injection fluid, wherein the flow conduit comprises: an inlet positioned on a side of the enhanced vapor injection fluid source to receive enhanced vapor injection fluid and an outlet positioned on a side of the intermediate pressure chamber to discharge the received enhanced vapor injection fluid; a tube wall; and a vane formed to extend obliquely from an inner wall surface of the pipe wall toward the outlet to suppress outward transmission of the pressure pulse in the intermediate-pressure chamber.
Alternatively, the blade is formed to extend obliquely in a circular arc shape or a straight line shape from the inner wall surface of the pipe wall toward the outlet.
Alternatively, in the case where the vanes are formed in a circular arc shape, the radius R1 of the vanes is in the range of 4mm to 7mm, and in the case where the vanes are formed in a straight shape, the acute included angle α formed between the vanes and the central axis of the draft tube is in the range of 20 ° to 70 °.
Alternatively, the vanes are formed as a single integral vane in a spiral shape or a plurality of segmented vanes in a spiral shape.
Alternatively, the inner wall surface of the pipe wall includes a first inner wall surface and a second inner wall surface which are oppositely disposed, and the blade is formed as a first blade extending from the first inner wall surface and a second blade extending from the second inner wall surface.
Optionally, there are a plurality of first vanes and a plurality of second vanes, the first vanes being arranged in series at an equal axial distance L1 and/or the second vanes being arranged in series at an equal axial distance L1.
Optionally, the ratio L1/D between the axial distance L1 and the inner diameter D of the draft tube is in the range of 0.5 to 2.
Optionally, the first and second vanes extend toward the central axis of the draft tube such that the free end of a first vane is spaced a predetermined radial distance L2 from the free end of an adjacent second vane.
Optionally, the predetermined radial distance L2 is in a range of 0.5mm to 3 mm.
Optionally, the first and second vanes are arranged in sequence with an axial distance L5 between adjacent first and second vanes.
Optionally, the ratio L5/D between the axial distance L5 and the inner diameter D of the draft tube is in the range of 0.5 to 2.
Optionally, the first and second vanes extend towards the central axis of the draft tube such that: the free ends of the first and second vanes extend beyond the central axis of the draft tube, whereby the first and second vanes partially overlap each other when viewed from the direction of the central axis of the draft tube.
Optionally, the radial distance L4 between the free tip of the first vane and the opposing inner wall surface of the tube wall is in the range of 2mm to 5mm, and/or the radial distance L4 between the free tip of the second vane and the opposing inner wall surface of the tube wall is in the range of 2mm to 5 mm.
Optionally, the free ends of the vanes are formed with a chamfer facing the outlet.
Optionally, the angled cut forms an acute angle β with the central axis of the draft tube in the range of 10 ° to 40 °, preferably, the angled cut forms an acute angle β with the central axis of the draft tube in the range of 18 ° to 22 °.
Optionally, the thickness h of the blade is in the range of 1mm to 3 mm.
Optionally, the outer wall surface of the draft tube is cylindrical, and the inner wall surface of the draft tube is circular or formed by two opposite arc surfaces and two opposite planes.
Optionally, the draft tube structure further comprises a liner tube, the draft tube being mounted in the liner tube.
Optionally, the compressor includes a fixed member defining a medium pressure cavity, one end of the liner tube being coupled to the fixed member such that the outlet is communicated to the medium pressure cavity, an outer conduit of the enhanced vapor injection conduit being coupled to the other end of the liner tube in abutment with the draft tube such that the inlet is communicated to the source of enhanced vapor injection fluid.
Optionally, the compressor comprises a fixed part defining a medium pressure chamber, in which a flow passage defining a flow duct is formed.
Optionally, the flow channel is a cuboid-shaped recess, and an inlet of an external conduit communicating to the enhanced vapor injection conduit and an outlet communicating to the intermediate pressure chamber are provided on a bottom surface of the flow channel.
Optionally, the draft tube structure further comprises a cover plate covering the flow passage to define the draft tube together with the flow passage.
According to another aspect of the present invention, there is also provided a non-orbiting scroll member of a scroll compressor implemented as the above-described fixed member to provide the above-described duct structure.
According to a further aspect of the present invention, there is also provided a compressor assembly having enhanced vapor injection, the compressor assembly comprising a compressor, a source of enhanced vapor injection fluid, and an enhanced vapor injection conduit adapted to supply enhanced vapor injection fluid from the source to a medium pressure chamber of the compressor, wherein the above-described conduit structure is disposed in the enhanced vapor injection conduit.
According to yet another aspect of the present invention, there is also provided a compressor system having enhanced vapor injection, wherein the compressor system comprises the above-described compressor assembly.
According to the diversion pipeline structure, the compressor assembly and the compressor assembly provided by the invention, in the using process of the diversion pipeline structure, the reverse flow of the enhanced vapor injection fluid in an enhanced vapor injection path can be obviously reduced or even eliminated under the condition that the influence on the forward flow of the enhanced vapor injection fluid is little or almost no, so that the vibration and the noise of a pipeline can be reduced under the condition that the forward flow efficiency of the enhanced vapor injection fluid is not reduced, and the valve body in the path is prevented from being damaged.
Drawings
Features and advantages of one or more embodiments of the present invention will become more readily apparent from the following description taken in conjunction with the accompanying drawings. The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way. The figures are not drawn to scale and some features may be exaggerated or minimized to show details of particular components. In the drawings:
FIG. 1 is a partial longitudinal cross-sectional view of a prior art compressor assembly having enhanced vapor injection;
FIG. 2 is a partial longitudinal cross-sectional view of a compressor assembly having enhanced vapor injection according to a first exemplary embodiment of the present invention;
FIG. 3 is a schematic illustration of a forward injection of fluid in a flow conduit structure according to a first exemplary embodiment of the present invention;
FIG. 4 is a schematic illustration of fluid reverse impingement in a flow conduit structure according to a first exemplary embodiment of the present invention;
FIG. 5 is a schematic perspective view of a copper elbow of an enhanced vapor injection conduit according to a first exemplary embodiment of the present invention;
FIG. 6 is a schematic perspective view of a liner of an enhanced vapor injection conduit according to a first exemplary embodiment of the present invention;
fig. 7a to 7d are schematic perspective views of an assembled delivery tube, first and second halves of the delivery tube, and cross-sectional views of the assembled delivery tube, respectively, according to a first exemplary embodiment of the present invention;
fig. 8 is a longitudinal sectional view of a flow conduit structure according to a first exemplary embodiment of the present invention;
FIG. 9 is a schematic perspective view of a non-orbiting scroll member according to a second exemplary embodiment of the present invention;
FIG. 10 is a schematic perspective view of a non-orbiting scroll member with a cover plate removed according to a second exemplary embodiment of the present invention;
FIGS. 11 a-11 b are perspective views of a bolt and cover plate of a non-orbiting scroll member according to a second exemplary embodiment of the present invention;
FIG. 12 is a partial schematic view of a flow passage of a non-orbiting scroll member according to a second exemplary embodiment of the present invention;
FIG. 13 is a longitudinal cross-sectional view of a non-orbiting scroll member according to a second exemplary embodiment of the present invention;
FIG. 14 is a top view of a flow passage of a non-orbiting scroll member according to a second exemplary embodiment of the present invention; and
fig. 15 is a schematic view of a guide vane according to a third exemplary embodiment of the present invention.
Detailed Description
Those skilled in the art will appreciate that enhanced vapor injection techniques may be applied to a variety of compressors, such as scroll compressors or gear compressors. For convenience of explanation, the associated enhanced vapor injection piping is described herein with a scroll compressor as an example. Preferred embodiments of the present invention will be described below with reference to the accompanying drawings, which are merely illustrative and not limitative of the present invention and its application.
The compressor system mainly comprises a compressor, a condenser, a main expansion valve and an evaporator. The working medium steam with lower pressure flowing out of the evaporator enters the air suction port of the compressor and is compressed, so that the temperature and the pressure of the working medium steam are both increased, and then the working medium leaves the air exhaust port of the compressor and enters the condenser. In the condenser, the working medium releases heat, condenses into liquid with normal temperature and higher pressure, throttles by the main expansion valve, becomes liquid with lower temperature and pressure, sends the liquid into the evaporator, absorbs heat in the evaporator to evaporate into vapor with higher temperature and lower pressure, and then sends the vapor into the air inlet of the compressor, thereby completing a working cycle. When the condenser is located indoors and the evaporator is located outdoors, the duty cycle may be considered a heating cycle. The compressor system may also have a four-way reversing valve such that the indoor heat exchanger functions as an evaporator and the outdoor heat exchanger functions as a condenser to achieve cooling of the indoor space, which will not be described in detail herein.
In cold regions, when the outdoor temperature is low, the heat exchange capacity of the outdoor evaporator is reduced, the amount of return air at the air inlet of the compressor is reduced, and the power of the compressor is reduced, and the best effect cannot be achieved. However, working medium (namely the enhanced vapor injection fluid) is supplemented through the intermediate pressure air supplement port on the compressor, so that the exhaust volume of the compressor is increased, the circulating working quality of indoor heat exchanger heating is increased, and the heating quantity is increased. This manner of increasing the amount of heat produced by the compressor is known as enhanced vapor injection. When the difference between the evaporation temperature (outdoor temperature) and the condensation temperature (indoor temperature) is larger, the better effect is generated, so the effect is more obvious in the low-temperature environment.
In order to achieve enhanced vapor injection, the compressor system is provided with an enhanced vapor injection path in addition to the working medium circulation path (main circuit) described above. In a compressor system provided with a vapor injection enthalpy path, an economizer (equivalent to a vapor injection enthalpy fluid source herein) is also provided, which includes, for example, an economizer expansion valve and a heat exchanger. The heat exchanger has a first passage and a second passage fluidly isolated from each other, and a portion of the working fluid from the condenser passes directly through the first passage of the heat exchanger and then into the main expansion valve. And the other part of working medium from the condenser sequentially passes through the economizer expansion valve and a second channel of the heat exchanger and returns to an air supplementing port of the compressor, which is communicated with the medium-pressure part. After being throttled by the economizer expansion valve, the temperature and the pressure of the second working medium part are both reduced, so that when the second working medium part enters a second channel of the heat exchanger, the second working medium part with relatively low temperature exchanges heat with the first working medium part, the temperature of the first working medium part is reduced, and the temperature of the second working medium part is properly increased. The path in the enhanced vapor injection compressor system downstream of the second pass of the heat exchanger is referred to as the enhanced vapor injection path.
By arranging the enhanced vapor injection path, on one hand, the working medium (the first working medium part) in the main loop is cooled before throttling so as to increase the enthalpy difference; on the other hand, the low-temperature low-pressure working medium (the second working medium part) throttled by the economizer expansion valve is preheated to reach the proper medium pressure and is supplied to the compressor for secondary compression, so that the compression process of the compressor is changed into a quasi-secondary compression process.
FIG. 1 is a partial longitudinal cross-sectional view of a prior art compressor assembly having enhanced vapor injection. As shown in fig. 1, the compressor assembly includes a compressor (shown in fig. 1 as a scroll compressor), a source of enhanced vapor injection fluid (not shown), and an enhanced vapor injection conduit adapted to supply enhanced vapor injection fluid from the source of enhanced vapor injection fluid to an intermediate pressure chamber of compressor 1. The scroll compressor 1 mainly includes a housing 13, a compression mechanism composed of a fixed scroll part 11 and an orbiting scroll part 12, and a drive mechanism. The compression mechanism is driven by a drive mechanism. Specifically, when the drive shaft of the drive mechanism rotates, orbiting scroll member 12 can be driven via the crank pin of the drive shaft such that orbiting scroll member 12 performs a translational rotation with respect to non-orbiting scroll member 11. The movable scroll part 12 and the fixed scroll part 11 form a plurality of closed compression cavities, and the compression cavities move from an inlet to an exhaust port of the compression mechanism along with the orbiting motion of the movable scroll part 12 relative to the fixed scroll part 11, the volume of the compression cavities is gradually reduced, and the pressure of the sucked working medium is gradually increased. The enhanced vapor injection pipeline 2 passes through a shell 13 of the compressor 1 and is fixedly connected with the shell 13 and the non-orbiting scroll part 11, and fluid in the enhanced vapor injection pipeline 2 enters an intermediate pressure cavity of the compressor 1 through a gas supplementing port on the non-orbiting scroll part 11. The flow direction of the fluid in the enhanced vapor injection conduit 2 into the intermediate-pressure chamber of the compressor 1 is defined herein as the forward direction. The pressure at the outlet of the enhanced vapor injection conduit 2 fluctuates because the position of the make-up gas port into the intermediate pressure chamber of the compressor 1 is fixed, while the pressure in the intermediate pressure chamber varies as the orbiting scroll orbits. Whereas at the inlet of the enhanced vapor injection conduit 2 the pressure of the fluid leaving the economizer is substantially constant, so the pressure difference between the inlet and the outlet creates a pressure pulsation in the enhanced vapor injection path. Here, the direction in which the fluid in the enhanced vapor injection pipeline 2 flows in the reverse direction due to the pressure pulsation is defined as a reverse direction. Such pressure pulsation easily causes severe shaking of each device (for example, a valve) on the pipeline or the pipeline itself, and not only generates noise, but also easily causes breakage of the pipeline connection.
In the prior art, a silencer is added on an enhanced vapor injection pipeline to reduce noise and vibration, but the mode causes the configuration of a compressor system to be complicated and the cost to be high. Or an expansion chamber may be provided in the compressor to reduce pressure pulsations, but this is often not desirable due to space limitations within the compressor. Or a check valve is arranged in the compressor to prevent the medium-pressure working medium from flowing reversely, however, the arrangement causes great pressure loss of forward injection and has the problem of reliability of the valve sheet.
Therefore, the invention provides a flow guide pipe structure for an enhanced vapor injection path. Referring to fig. 2, in the compressor assembly having enhanced vapor injection according to the first exemplary embodiment of the present invention, the structure and operation principle of the compressor 1 are substantially the same as those of the scroll compressor in fig. 1, and thus, a detailed description thereof will be omitted. The enhanced vapor injection pipeline 20 connected with the compressor 1 mainly comprises an elbow 21, a liner 22 and a draft tube 23. The liner 22 is fixed to the casing 13 of the compressor 1 by passing through the casing 13, and has a first end portion extending inside the compressor 1 to be connected to the non-orbiting scroll member 11 and in fluid communication with a supplementary air port of the non-orbiting scroll member 11 communicating with the intermediate pressure chamber, and a second end portion opposite to the first end portion extending outside the compressor 1 to be connected to the elbow 21. With reference to fig. 6, the liner 22 is substantially cylindrical, with a first end having a portion of reduced diameter, whose junction with the rest of the liner 22 forms a step surface for abutment and positioning of the draft tube 23 on the one hand, and for maintaining the portion of internal diameter substantially the same as or slightly smaller than that of the draft tube 23 and the elbow 21 on the other hand. A circular boss is formed on the second end of the liner tube 22 for locating the liner tube 22 against the exterior of the shell 13 of the compressor and for welding between the liner tube 22 and the shell 13. The liner 22 is preferably a metal liner and is preferably welded to the housing 13.
The draft tube 23 is installed inside the liner tube 22. The delivery tube 23 is preferably a clearance fit with the liner 22, however other fits are possible, such as an interference fit. The inner wall surface of the draft tube 23 is provided with a plurality of pairs of blades arranged at certain intervals along the axial direction of the draft tube 23, wherein two blades 233 of each pair of blades are respectively arranged at two sides of a plane passing through the axial direction of the draft tube 23, and the two blades 233 of each pair of blades can be symmetrically arranged relative to the plane or staggered. Each vane 233 extends obliquely from the inner wall surface of the pipe wall toward the outlet of the draft pipe. The outer wall surface of the draft tube 23 is cylindrical and fitted to the inner wall surface of the draft tube 23, and the inner wall surface of the draft tube 23 is not limited to a circle. The flow guide tube 23 may be divided into two symmetrical halves for processing or may be integrally formed. Fig. 7a to 7d show a flow guide tube 23 which is divided into two halves for processing. Fig. 7a is a perspective view of the two halves of the flow duct 23 assembled together, fig. 7b and 7c are perspective views of the first half 231 and the second half 232 of the flow duct, respectively, and fig. 7d is a cross-sectional view of the flow duct 23 in the radial direction. In the example shown in fig. 7a to 7d, the inner wall surface of the flow guide tube 23 is formed by two opposite circular arc surface sections 234 and two opposite flat surface sections 235 connected together. The two blades 233 of each pair are formed on two arc surface segments 234, respectively. The first half 231 of the duct is mirror-symmetrical to the second half 232, wherein the first half 231 has a wall portion, the inner wall surface of which is formed by one half of two opposite circular arc surface sections 234 and one flat section 235, and a vane portion, which is formed by one half 2311 of two vanes 233 in each pair of vanes. When the first half 231 and the second half 232 of the draft tube are assembled together and attached to the liner 22, the complete vane 233 and the smooth inner wall surface of the draft tube 23 are formed. The flow duct 23 is preferably a metal part, more preferably an aluminum casting, but may also be a plastic part.
One end of the elbow 21 is mounted within the liner 22 and abuts the draft tube 23, while the other end is connected to an external enhanced vapor injection fluid source (e.g., economizer, etc.). Referring to fig. 5, elbow 21 is preferably a copper elbow and is welded to liner 22 and to the piping of the enhanced vapor injection fluid source.
Fig. 3 and 4 show the flow paths of the respective fluids in the enhanced vapor injection conduit, in particular the draft tube. When the fluid is injected in the forward direction from the external enhanced vapor injection fluid source into the intermediate pressure chamber of the compressor, the fluid flows into the intermediate pressure chamber with little or negligible pressure loss due to the vanes 233 in the draft tube 23 extending obliquely from the inner wall surface of the tube wall toward the outlet of the draft tube 23. When the fluid flows in the opposite direction of the enhanced vapor injection fluid source from the intermediate pressure chamber to the outside due to the pressure pulsation, the vane 233 greatly obstructs the flow of the fluid, thereby causing the flow in the opposite direction to be blocked, even isolating the effect of the pressure pulsation on the enhanced vapor injection conduit.
In order to obtain a better effect of guiding the fluid in the forward direction and of hindering the fluid in the reverse direction, the detailed dimensions of the flow duct 23 are described below with reference to fig. 8, fig. 8 is a longitudinal sectional view of the flow duct 23, in which the cross section of the vanes 233 in the direction along the axis of the flow duct 23 and through the centre of the vanes is circular-arc-shaped, the radius R1 of which is preferably in the range of 4mm to 7mm, the thickness h of the vanes 233 is preferably in the range of 1mm to 2.5mm, each vane 233 of each pair of vanes 233 extends obliquely from the inner wall surface of the duct wall towards the outlet of the flow duct 23 and to the position where the free end of the vane is at a radial distance L2, preferably a radial distance L2 in the range of 0.5mm to 3mm, the ratio L1/D of the axial distance L1 between adjacent vanes 233 on the same side of the plane passing through the axis of the flow duct 23 to the inner diameter D of the flow duct 23 is preferably in the range of 0.5 to 2.
The inventors measured the pressure in the prior art enhanced vapor injection path, first, as shown in fig. 1, and the pressure in the enhanced vapor injection path according to the first embodiment of the present invention, second, as shown in fig. 2-8, and compared the above-mentioned pressure first and pressure second curves over time, and observed that the pressure first exhibited significant pulse fluctuations, while the pressure second was more stationary and the amplitude of the pressure pulses was significantly reduced. While the amplitude of the pressure pulses is significantly reduced in each frequency domain (e.g., at 100Hz, 200Hz, 400Hz, and 600 Hz). It can be seen that the draft tube according to the first embodiment of the present invention can prevent the fluid from flowing reversely in the enhanced vapor injection path, and significantly improve the noise and vibration of the compressor due to the pressure pulsation.
The pressure pulsation can be reduced or even eliminated by arranging the flow passage structure with the guide vanes in the enhanced vapor injection path, but the flow passage structure with the guide vanes is not limited to be arranged in the enhanced vapor injection path in a guide pipe manner, and can also be integrated on the fixed scroll part. Fig. 9 to 14 show a second embodiment according to the present invention, mainly relating to a non-orbiting scroll member with a flow passage structure including guide vanes.
FIGS. 9 and 10 are perspective views of the non-orbiting scroll member 11 with the cover plate 2032 installed and the cover plate 2032 removed, respectively, except for the arrangement of the flow channel structure with respect to the guide vanes, the main structure of the non-orbiting scroll member 11 is substantially the same as that of the non-orbiting scroll member 11 in the prior art and the first embodiment of the present invention, hereinafter, only the description will be given mainly with respect to the arrangement of the flow channel structure with respect to the guide vanes on the non-orbiting scroll member 11. the non-orbiting scroll member 11 has a base plate 111 and a wrap 112 extending on the lower surface of the base plate 111. the base plate 111 is provided with a groove formed by recessing from the upper surface of the base plate 111 toward the inside thereof. furthermore, referring to FIGS. 11a and 11b, a cover plate 2032 is further provided, the cover plate 2032 covers the flow channel 203 and is fixed to the base plate 111 by a screw 3 passing through an aperture on the cover plate 2032 to define the flow channel 203 together with the above groove.A. the groove of the channel 203 is rectangular parallelepiped shape and size of which the groove 203 is provided with pairs of vanes 2031 at the same interval in the longitudinal axis of the groove 203 along the longitudinal axis of the channel 203. the groove 2033, and the length of the other vanes 2033 of the longitudinal axis of the groove 2033, such as the longitudinal direction of the longitudinal channel 203, such as the longitudinal axis of the longitudinal dimension of the longitudinal.
Referring to fig. 12 and 13, injection ports 2034 are opened on a circumferential side surface of the base plate 111 of the non-orbiting scroll part 11, and an enhanced vapor injection pipe is connected to the injection ports 2034. An inlet 2036 and an outlet 2035 are provided on the bottom surface of the flow passage 203, the inlet 2036 is provided near the short sidewall of the injection port 2034, and the inlet 2036 is in fluid communication with the injection port 2034, the outlet 2035 is provided near the short sidewall opposite to the position of the inlet 2036, and the outlet 2035 is in fluid communication with the middle pressure chamber of the compression mechanism. The vanes 2031 are disposed between the inlet 2036 and the outlet 2035.
The flow path 203 is not limited to the rectangular parallelepiped shape as shown in fig. 9 to 14, and may be formed directly inside the base plate 111 of the fixed scroll member 11 as the flow path of the flow guide tube 23, that is, a cylindrical flow path with the blades 233 or a flow path formed by an arc surface section and a flat surface section may be formed inside the base plate 111. In this case, the inlet of the flow channel is formed on the circumferential side surface of the base plate 111 and is connected to the enhanced vapor injection conduit, and the outlet of the flow channel is in fluid communication with the intermediate pressure chamber of the compression mechanism.
According to the flow channel arrangement of the second embodiment of the invention, the pressure pulse amplitude in the enhanced vapor injection path can be effectively reduced, so that the noise and the vibration are reduced, and the flow channel is directly integrated on the fixed scroll part, so that the number of parts is reduced, and the requirements on assembly and machining precision are lowered.
With regard to the arrangement and shape of the vanes in the flow channel, there are other forms than those described above. Figure 15 shows an optimised blade form. Wherein, a plurality of vanes 331 are arranged on the inner wall surface of the draft tube 33 at regular intervals in the axial direction of the draft tube 33, the vanes 331 extend obliquely from the inner wall surfaces on both sides of a plane passing through the axial line of the draft tube 33 toward the outlet of the draft tube 33 in turn alternately, and each vane 331 is arranged to be offset from the adjacent vane with respect to the above-mentioned plane.
The cross-section of the vane 331 in the direction along the axis of the draft tube 33 and through the center of the vane is linear, the vane 331 is formed at a first end connected to the inner wall surface of the draft tube 33 with a first curved surface portion smoothly transitioning from the inner wall surface, and at a second end opposite the first end with a second curved surface portion extending in the forward direction, the second curved surface portion also being formed with an angled surface facing the outlet of the draft tube 33, the acute angle β between the angled surface and the central axis of the draft tube 33 being preferably in the range of 10 ° to 40 °, preferably the acute angle β between the angled surface and the central axis of the draft tube 33 being preferably in the range of 18 ° to 22 °, and the angle α between the vane 331 and the central axis of the draft tube 33 being preferably in the range of 20 ° to 70 °, the thickness h of the vane 331 being preferably in the range of 1mm to 3mm, the vane 331 extends toward the axis of the draft tube 33 to its free end beyond the central axis of the draft tube 33 and extends to the radial distance 34 between the tip of the opposing inner wall, whereby the radial distance between the vane 33D 5, the radial distance D of the vane 33, the radial distance D, when viewed from the axial section of the draft tube 33, the section of the draft tube 33, the section, preferably the section, and the section of the draft tube 33, and the section of the draft tube 33, which are preferably the section, which is in the section, which is illustrated in the section, and the.
The vane form shown in fig. 15 is not limited to being provided in the draft tube, but can be applied to the second embodiment of the present invention as shown in fig. 9 to 14, in which case the inner diameter D of the draft tube 33 corresponds to the length L3 of the short sidewall of the rectangular parallelepiped-shaped flow path 203 and the radial direction corresponds to the direction along the short sidewall, and further, the vane form described in the third embodiment is not limited to being entirely applied to the draft tube or the flow path instead of the vane of the circular arc shape, but a single feature or a combination of partial features may be alternatively or additionally applied to the first and second embodiments, for example, the vane of the circular arc shape may also be formed in a form having a chamfered surface or in a form in which the free tip of the vane exceeds the central axis of the draft tube.
The inventors have tested that the vane form described in the third embodiment also reduces the amplitude of the pressure pulses in the enhanced vapor injection path even better, thereby reducing noise and vibration considerably and avoiding damage to the valve member in the enhanced vapor injection path.
The invention is susceptible of various possible variations. For example, the vanes may be provided as integral or segmented helical vanes extending in the forward direction of the draft tube for directing the enhanced vapor injection fluid flowing in the forward direction and impeding its reverse flow. For example, the structure of the flow guide tube with the blades may be not only embedded in the compressor or integrated completely, but also be disposed completely outside the compressor, as long as it is disposed on the enhanced vapor injection path.
Although various embodiments of the present invention have been described in detail herein, it is to be understood that this invention is not limited to the particular embodiments described and illustrated in detail herein, and that other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the invention. All such variations and modifications are intended to be within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent components.
Claims (26)
1. A flow conduit structure for a compressor assembly having enhanced vapor injection, the compressor assembly comprising a compressor, a source of enhanced vapor injection fluid and an enhanced vapor injection conduit adapted to supply enhanced vapor injection fluid from the source of enhanced vapor injection fluid to a medium pressure chamber of the compressor, the flow conduit structure comprising a flow conduit (23,33), the flow conduit (23,33) disposed in the enhanced vapor injection conduit and defining at least a portion of a flow path for enhanced vapor injection fluid, wherein the flow conduit (23,33) comprises:
an inlet on a side of the enhanced vapor injection fluid source for receiving enhanced vapor injection fluid and an outlet on a side of the intermediate pressure chamber for discharging the received enhanced vapor injection fluid;
a tube wall; and
a vane (233,2033,331) formed to extend obliquely from an inner wall surface of the pipe wall toward the outlet to suppress outward transmission of pressure pulses in the intermediate pressure chamber.
2. The nozzle structure according to claim 1, wherein the vane is formed to extend obliquely from an inner wall surface of the pipe wall toward the outlet in a circular arc shape or a straight line shape.
3. The draft tube structure of claim 2, wherein in the case where the vane is formed in a circular arc shape, a radius R1 of the vane (233,2033) is in the range of 4mm to 7mm, and in the case where the vane is formed in a straight line shape, an acute included angle α formed between the vane (331) and a central axis of the draft tube (23,33) is in the range of 20 ° to 70 °.
4. The nozzle arrangement according to claim 1, wherein the vane (233,2033,331) is formed as a single unitary vane in a spiral shape or as a plurality of segmented vanes in a spiral shape.
5. The nozzle structure according to claim 1, wherein the inner wall surface of the tube wall includes a first inner wall surface and a second inner wall surface that are oppositely disposed, and the vane is formed as a first vane extending from the first inner wall surface and a second vane extending from the second inner wall surface.
6. The nozzle structure of claim 5, wherein the first vanes and the second vanes are each a plurality of, the first vanes being arranged sequentially at equal axial distances L1, and/or the second vanes being arranged sequentially at equal axial distances L1.
7. A duct structure according to claim 6, wherein the ratio L1/D between the axial distance L1 and the inner diameter D of the duct (23) is in the range of 0.5 to 2.
8. A nozzle arrangement according to claim 5, wherein the first and second vanes extend towards the central axis of the nozzle (23) such that the free tip of the first vane is spaced from the free tip of the adjacent second vane by a predetermined radial distance L2.
9. A nozzle structure according to claim 8, wherein the predetermined radial distance L2 is in the range 0.5mm to 3 mm.
10. The nozzle structure of claim 5, wherein the first vanes are three in number and the second vanes are three in number.
11. The nozzle structure of claim 5, wherein the first and second vanes are arranged in sequence with an axial distance L5 between adjacent first and second vanes.
12. The draft tube structure of claim 11, wherein a ratio L5/D between said axial distance L5 and an inner diameter D of said draft tube (23) is in the range of 0.5 to 2.
13. A duct structure according to claim 5, wherein the first and second vanes extend towards the central axis of the duct (23) such that: the free ends of the first and second vanes extend beyond the central axis of the draft tube (23), whereby the first and second vanes partially overlap each other when viewed in the direction of the central axis of the draft tube (23, 33).
14. A nozzle arrangement according to claim 13, wherein the radial distance L4 between the free tip of the first vane and the opposing inner wall surface of the tube wall is in the range 2mm to 5mm and/or the radial distance L4 between the free tip of the second vane and the opposing inner wall surface of the tube wall is in the range 2mm to 5 mm.
15. A nozzle arrangement according to any of claims 1 to 14, wherein the free tips of the vanes are formed with a chamfer facing the outlet.
16. A duct structure according to claim 15, wherein the chamfer forms an acute included angle β in the range 10 ° to 40 ° with the central axis of the duct (23, 33).
17. The nozzle structure according to any of claims 1-14, wherein the thickness h of the vane (331) is in the range of 1-3 mm.
18. The draft tube structure according to any one of claims 1 to 14, wherein an outer wall surface of the draft tube (23,33) is cylindrical, and an inner wall surface of the draft tube (23,33) is circular or formed of two opposite arc surfaces and two opposite flat surfaces.
19. A nozzle arrangement according to any of claims 1-14, wherein the nozzle arrangement further comprises a liner (22), the nozzle (23,33) being mounted in the liner (22).
20. A draft tube arrangement according to claim 19, wherein the compressor includes a fixed part defining the intermediate pressure chamber, one end of the liner (22) being coupled to the fixed part such that the outlet communicates to the intermediate pressure chamber, an outer one of the enhanced vapor injection conduits being coupled to the other end of the liner (22) in abutment with the draft tube (23,33) such that the inlet communicates to the source of enhanced vapor injection fluid.
21. A duct structure according to any of claims 1-14, wherein the compressor comprises a stationary part defining the medium-pressure chamber, in which stationary part a flow channel (203) defining the duct (23,33) is formed.
22. A flow conduit arrangement according to claim 21, wherein the flow channel (203) is a cuboid shaped groove, the inlet (2036) to an outer conduit of the enhanced vapor injection conduit and the outlet (2035) to the intermediate pressure chamber being provided on a bottom surface of the flow channel (203).
23. A duct arrangement according to claim 21, wherein the duct arrangement further comprises a cover plate (2032), the cover plate (2032) covering the flow channel (203) to define the duct (23,33) together with the flow channel (203).
24. Non-orbiting scroll component of a scroll compressor, wherein the non-orbiting scroll component is implemented as a fixed component according to any one of claims 21 to 23 so as to be provided with a draft tube structure according to any one of claims 21 to 23.
25. A compressor assembly having enhanced vapor injection, the compressor assembly comprising a compressor, a source of enhanced vapor injection fluid, and an enhanced vapor injection conduit adapted to supply enhanced vapor injection fluid from the source to a medium pressure chamber of the compressor, wherein the enhanced vapor injection conduit has disposed therein a flow conduit structure according to any one of claims 1 to 23.
26. A compressor system having enhanced vapor injection, wherein the compressor system comprises the compressor assembly of claim 25.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910066927.8A CN111472978A (en) | 2019-01-24 | 2019-01-24 | Flow guide pipe structure, fixed scroll part, compressor assembly and compressor system |
| PCT/CN2019/121485 WO2020151365A1 (en) | 2019-01-24 | 2019-11-28 | Flow guide pipe structure, non-orbiting scroll member, compressor assembly, and compressor system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910066927.8A CN111472978A (en) | 2019-01-24 | 2019-01-24 | Flow guide pipe structure, fixed scroll part, compressor assembly and compressor system |
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| CN111472978A true CN111472978A (en) | 2020-07-31 |
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| CN201910066927.8A Pending CN111472978A (en) | 2019-01-24 | 2019-01-24 | Flow guide pipe structure, fixed scroll part, compressor assembly and compressor system |
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| CN111963423A (en) * | 2020-08-31 | 2020-11-20 | 广东美芝制冷设备有限公司 | Static scroll assembly, scroll compressor and refrigeration equipment |
| CN111963425A (en) * | 2020-08-31 | 2020-11-20 | 广东美芝制冷设备有限公司 | Static scroll assembly, scroll compressor and refrigeration equipment |
| CN111963424A (en) * | 2020-08-31 | 2020-11-20 | 广东美芝制冷设备有限公司 | Static scroll assembly, scroll compressor and refrigeration equipment |
| WO2022027852A1 (en) * | 2020-08-06 | 2022-02-10 | 艾默生环境优化技术(苏州)有限公司 | Enhanced-vapor-injection sleeve assembly and compressor |
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