WO2020057535A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

Info

Publication number
WO2020057535A1
WO2020057535A1 PCT/CN2019/106376 CN2019106376W WO2020057535A1 WO 2020057535 A1 WO2020057535 A1 WO 2020057535A1 CN 2019106376 W CN2019106376 W CN 2019106376W WO 2020057535 A1 WO2020057535 A1 WO 2020057535A1
Authority
WO
WIPO (PCT)
Prior art keywords
section
bypass
valve
scroll compressor
scroll
Prior art date
Application number
PCT/CN2019/106376
Other languages
English (en)
French (fr)
Inventor
张琼宇
刘轩
Original Assignee
艾默生环境优化技术(苏州)有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Publication of WO2020057535A1 publication Critical patent/WO2020057535A1/zh

Links

Images

Classifications

    • 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
    • F04C18/0223—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 with symmetrical double wraps
    • 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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • 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
    • F04C29/12—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
    • 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
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps

Definitions

  • the present disclosure relates to the technical field of scroll compressors, and more particularly, to a scroll compressor having a variable volume ratio.
  • a climate control system such as a heat pump system, a refrigeration system, or an air conditioning system, may include a fluid circuit having an outdoor heat exchanger, an indoor heat exchanger, and disposed between the indoor heat exchanger and the outdoor heat exchanger.
  • a working fluid eg, a refrigerant
  • Scroll compressors with variable volume ratio (VVR) are often used in such systems to match the pressure ratio of the compressor to the operating pressure required by the system to avoid over-compression.
  • a scroll compressor belongs to a typical positive displacement compressor.
  • the compression mechanism of a scroll compressor usually includes a fixed scroll component and a movable scroll component, and the scroll blades of the fixed scroll component and the movable scroll component cooperate with each other to form a series of compression cavities so that the working fluid (also called Compresses a working fluid, such as a gaseous refrigerant, and the compressed high-pressure gas is discharged to the exhaust passage through the exhaust passage to exhaust the pressure zone.
  • the working fluid also called Compresses a working fluid, such as a gaseous refrigerant
  • a bypass passage connecting the intermediate compression cavity and the exhaust passage is provided on the end plate of the fixed scroll component.
  • the bypass passage is provided with a check valve at the outlet communicating with the exhaust passage. (Bypass valve), the pressure in the exhaust channel and the exhaust pressure zone corresponds to the operating pressure of the system.
  • the required working pressure of the system is low, the pressure in the middle cavity is sufficient to open the check valve, and the medium-pressure gas that has not been fully compressed is discharged to the exhaust pressure zone, and the compressor operates at a low volume ratio.
  • the required working pressure is high, the bypass valve remains closed, and the compressor operates at a high volume ratio.
  • the degree of freedom in designing the bypass passage is very low. Not only limits the adjustment capacity of the design volume ratio, but also limits the design of the bypass valve itself.
  • the axially extending intermediate pressure gas inlet of the bypass passage needs to communicate with the axially extending intermediate pressure gas outlet, so the installation position of the intermediate pressure gas inlet is also restricted, which also limits the ability to adjust the design volume ratio.
  • An object of the present disclosure is to provide a variable volume ratio scroll compressor capable of avoiding loss of system efficiency caused by over-compression.
  • Another object of the present disclosure is to provide a scroll compressor with a high variable volume ratio design freedom, particularly a wider volume ratio design range, to improve the operating efficiency of a system including the compressor.
  • a scroll compressor including a first scroll member including a first end plate and a first scroll extending from the first end plate.
  • the rotating blades mesh to form a series of compression cavities, which includes a suction cavity, a plurality of intermediate cavities, and a discharge cavity.
  • the first end plate includes a bypass passage extending through the first end plate. One end of the bypass passage is in communication with the exhaust passage via a bypass port and the other end is in communication with the intermediate cavity. The position of the bypass port is deviated in a radial direction from a position where the bypass passage communicates with the intermediate cavity.
  • the bypass passage may include a first section and a second section communicating with each other, the first section leading to the intermediate cavity, and the second section leading to the Exhaust channel.
  • the bypass passage may further include a laterally extending connecting section connecting the first section and the second section.
  • the first end plate may include a first annular wall surrounding a first region on a side opposite to the first scroll blade, the first annular wall defining the exhaust passage.
  • the first end plate may further include a discharge passage extending through the first end plate, one end of the discharge passage communicates with the exhaust passage via a discharge port and the other end communicates with the discharge cavity.
  • the discharge port and the bypass port are both disposed in the first region.
  • a bypass valve may be provided at the bypass port, and the bypass valve is a one-way valve.
  • the bypass path may include a first set of bypass paths and a second set of bypass paths, the first set of bypass paths include one or more first bypass paths, and the second The group bypass path includes one or more second bypass paths.
  • the first section is one or more, the second section is one or more, the first section and the The second section can be directly connected by one of said connecting sections.
  • the first section is one or more, the second section is one or more, and the first section and the second section can pass through One of said connecting sections is directly connected.
  • the first set of bypass paths includes a plurality of first bypass paths
  • the connection section may include a first connection section and a second A connecting section
  • the first connecting section is in direct communication with part or all of the first section
  • the second connecting section is in communication with the remaining first section, the first connecting section, and
  • the second section is directly connected.
  • the second group of bypass passages includes a plurality of second bypass passages.
  • the connection section may include a first connection section and a second connection section. The first connection section is in direct communication with part or all of the first section, and the second connection section is in communication with the remaining first section, the first connection section, and the second section Direct connectivity.
  • the one or more first bypass paths may include a corresponding one or more of the second sections, and the one or more second bypass paths may include a corresponding one or A plurality of said second sections.
  • the one or more first bypass paths may share a second section, and the one or more second bypass paths may share a second section.
  • the one or more first bypass paths and the one or more second bypass paths may share one of the second section and one of the bypass ports.
  • a discharge valve may be provided at the discharge port and a bypass valve may be provided at the bypass port, and the discharge valve and the bypass valve are check valves.
  • the bypass valve may be provided separately from the discharge valve.
  • the bypass valve and the discharge valve may be provided as an integrated valve in which at least one of a valve plate, a valve member, a valve stop, and a biasing member is a common member.
  • the first section may be disposed radially outward of the first region away from the second section in a radial direction.
  • connection section may include an effective volume section and an ineffective volume section, and the ineffective volume section extends from an opening position of the connection section to a communication position communicating with other sections.
  • the scroll compressor may further include a plug for eliminating the dead volume section.
  • one end face of the plug may include a tool engaging groove for engaging with a tool to insert the plug into the ineffective volume section.
  • the connecting section may include internal threads over the entire length of the ineffective volume section, the plug is in the shape of a stud with external threads, and the length of the plug is less than the length of the plug
  • the length of the ineffective volume section can be obtained by screwing the plug into the ineffective volume section and fixing it at a position adjacent to the ineffective volume section. A segment is isolated from the effective volume segment.
  • the connecting section may be formed with an internal thread only at an opening position thereof, the plug is in the shape of a stepped column and includes a first cylindrical portion and a diameter slightly smaller than the first cylindrical portion.
  • a second cylindrical portion having an external thread formed on the outer peripheral surface of the first cylindrical portion for engagement with the internal thread, and the length of the second portion is set to be able to fill the ineffective volume section.
  • the first end plate may further include a second annular wall on a radially outer side of the first annular wall, and a back pressure chamber is defined between the first annular wall and the second annular wall. And the back pressure chamber communicates with one of the intermediate cavities via a back pressure passage extending through the first end plate, the intermediate cavity communicating with the back pressure passage is different from the bypass passage Connected middle cavity.
  • the exhaust passage may communicate with an exhaust pressure region of the scroll compressor via a check valve.
  • a scroll compressor having a variable volume ratio makes it possible to improve the variable volume ratio performance and significantly increase the efficiency of the entire system including the compressor by improving the design of the bypass passage that increases the middle lateral section.
  • the scroll compressor according to the present disclosure can increase the design freedom of the size, shape, and position of the bypass passage without increasing the size of the compressor, thereby improving the capacity of adjusting the volume ratio and the bypass valve itself.
  • FIG. 1 is a schematic longitudinal sectional view of an example compressor having a variable volume ratio
  • FIG. 2 is a partially cutaway perspective exploded view showing a fixed scroll component and a bypass valve of the compressor shown in FIG. 1;
  • FIG. 3a is a perspective view of a bypass passage according to an embodiment of the present disclosure
  • FIG. 3b is a schematic longitudinal sectional view of a fixed scroll member to which the bypass passage shown in FIG. 3a is applied;
  • FIG. 4a is a perspective view of a bypass passage according to another embodiment of the present disclosure
  • FIG. 4b is a schematic longitudinal sectional view of a fixed scroll member to which the bypass passage shown in FIG. 4a is applied;
  • FIG. 5 is a partially cutaway perspective view of the fixed scroll member shown in FIG. 4b;
  • FIG. 6 is a cross-sectional view of the fixed scroll member shown in FIG. 4b at the intermediate connection section;
  • FIG. 7 is a cross-sectional view of a fixed scroll member at an intermediate connection section according to another embodiment of the present disclosure.
  • FIG. 8 is a perspective view of a fixed scroll component of a compression mechanism similar to FIG. 2 according to another embodiment of the present disclosure
  • FIG. 9a is a cross-sectional view of a plug according to an embodiment of the present disclosure
  • FIG. 9b is a partially cutaway perspective view of a bypass passage in which the plug of FIG. A cross-sectional view of the pathway;
  • FIG. 10a is a cross-sectional view of a plug according to another embodiment of the present disclosure
  • FIG. 10b is a partially cutaway perspective view of a bypass passage in which a plug of FIG. 10a is installed at a connecting section
  • FIG. 10c is a side view shown in FIG. 10b Cross-section view of a via.
  • Example embodiments are provided so that this disclosure will be thorough and fully convey the scope to those skilled in the art. Numerous specific details are set forth, such as examples of specific components, devices, and methods to provide a comprehensive understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be implemented in many different forms, and should not be construed as limiting the scope of the disclosure. In some example embodiments, well-known methods, well-known device structures, and well-known technologies are not described in detail.
  • first, second, third, etc. will be used herein to describe different elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms . These terms may be used only to distinguish one element, component, region, layer and / or section from another region, layer and / or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or sequence unless clearly indicated by context. Thus, a first element, component, region, layer, or section discussed below can be termed a second element, component, region, layer, or section without departing from the teachings of the exemplary embodiments.
  • the compressor 10 may include a housing, a refrigerant discharge joint 14, an intake inlet joint (not shown), a motor assembly, a bearing seat assembly, a compression mechanism, a retaining assembly, a seal assembly, and a valve assembly.
  • the housing can house the motor assembly, bearing block assembly, and compression mechanism.
  • the housing may include: a longitudinally extending housing 30 having a suction inlet (not shown); an end cover 34 having an exhaust outlet 36; a laterally extending partition 37; and a base 38.
  • the end cover 34 may be fixed to the upper end of the casing 30.
  • the base 38 may be fixed to the lower end of the casing 30.
  • the end cover 34 and the partition plate 37 may generally define an exhaust pressure region, and the partition plate 37, the housing 30, and the base 38 may generally define an intake pressure region.
  • the motor component, the bearing block component and the compression mechanism are arranged in the suction pressure area.
  • the partition 37 includes an orifice 39 that provides communication between the compression mechanism and the exhaust pressure region.
  • the exhaust pressure region may generally form an exhaust muffler of the compressor 10.
  • the refrigerant discharge joint 14 may be attached to the housing at an exhaust outlet 36 in the end cover 34.
  • the suction inlet joint may be attached to the housing 30 at the suction inlet.
  • the motor assembly may generally include a stator 44, a rotor 46, and a drive shaft 48.
  • the stator 44 can be press-fitted into the housing 30 and drives the rotor 46 to rotate through electromagnetic interaction with the rotor 46.
  • the rotor 46 can be press-fitted on the drive shaft 48.
  • the drive shaft 48 is rotatably driven by a rotor 46 and is supported by a bearing block assembly.
  • a lubricating oil passage 50 is formed in the driving shaft 48 to supply lubricating oil from an oil pool formed at the base 38 to an upper bearing seat assembly and a compression mechanism to provide lubrication.
  • the drive shaft 48 may include an eccentric crank pin 52 having a flat portion thereon for driving engagement with a compression mechanism.
  • the bearing block assembly may include a lower bearing block 56 and a main bearing block 54 fixed within the housing 30.
  • the compression mechanism may be driven by a motor assembly, and may generally include a movable scroll member 60 and a fixed scroll member 62.
  • the movable scroll member 60 may include an end plate 64 and a movable scroll blade 66 extending vertically upward from an upper surface of the end plate 64.
  • the fixed scroll member 62 may include an end plate 74 and a fixed scroll blade 78 extending vertically downward from a lower surface of the end plate 74.
  • the fixed scroll blade 78 may be engaged with the movable scroll blade 66, thereby forming a series of compression cavities.
  • the volume of these compression cavities will vary throughout the compression cycle of the compression mechanism, and may include a suction cavity located at the outermost side in the radial direction, several intermediate cavities, and a central discharge cavity.
  • the fixed scroll member 62 may include a first annular wall 80 on the other side of the end plate 74 opposite to the side where the fixed scroll blade 78 is located.
  • the first annular wall 80 surrounds the first region 84 which is substantially circular, and the discharge port 88 and the bypass port 90 may be disposed in the first region.
  • the discharge port 88 may communicate with the discharge cavity via a discharge passage (exhaust port) 89, and the bypass port 90 may communicate with the intermediate cavity via a bypass passage 91.
  • the first annular wall 80 defines an exhaust passage 20 on its radially inner side, and the exhaust passage 20 selectively communicates with the exhaust cavity via the exhaust port 88 and the exhaust passage 89 and communicates with the intermediate cavity via the bypass port 90 and the bypass passage 91. Point connected.
  • the bypass port 90 is shown as including three first bypass ports 90 a and three second bypass ports 90 b formed substantially symmetrically with respect to the central discharge port 88 to Ensures that the compressor switches steadily and efficiently between low and high compression ratios.
  • the first bypass port 90a communicates with one intermediate cavity via the first bypass passage 91a
  • the second bypass port 90b communicates with another intermediate cavity on the opposite side via the second bypass passage 91b.
  • Each bypass port can Corresponds to a bypass path, see Figure 5.
  • the fixed scroll member 62 may further be provided with a second annular wall 82 on a radially outer side of the first annular wall 80.
  • a substantially annular second region 86 is enclosed between the first annular wall 80 and the second annular wall 82.
  • the back pressure chamber 93 may be provided in a second region 86 located between the first annular wall 80 and the second annular wall 82 in the radial direction, and the back pressure chamber 93 may be connected to the compression mechanism via a back pressure passage (not shown).
  • One of the intermediate cavities communicates and establishes back pressure in the back pressure chamber 93. Therefore, the fixed scroll member 62 and the movable scroll member 60 are kept against each other during the compression mechanism of the compression mechanism, and the axial flexibility of the scroll member is provided in cooperation with the holding assembly, thereby ensuring the safe and reliable operation of the compressor. .
  • the retaining assembly may generally include a sleeve 18 and a fastener 16 extending through the fixed scroll member 62.
  • the fastener 16 may be fixed to the main bearing block 54.
  • the fixed scroll member 62 can be fixed relative to the main bearing block 54 by a holding assembly that allows the fixed scroll member 62 to have a limited axial displacement based on the back pressure of the back pressure chamber 93.
  • a seal assembly (e.g., a floating seal assembly provided in the back pressure chamber 93) is used to sealingly engage the first and second annular walls 80, 82 and the partition plate 37 to bring the back pressure chamber 93 into a low pressure region and a high pressure of the compressor 10. Zone isolation.
  • the valve assembly may include a bypass valve 13 for controlling the opening and closing of the bypass port 90, and the bypass valve 13 is a one-way valve.
  • FIG. 2 An exploded view of the bypass valve 13 is shown in FIG. 2.
  • the bypass valve 13 may include a valve plate 130, a valve member 132, a valve stop 133, and a biasing member 134.
  • the valve plate 130 may be positioned above the bypass port 90 such that the drain port 88 and the bypass port 90 are exposed through an orifice on the valve plate 130.
  • the valve stop 133 may be fixed to the valve plate 130 by a fastener such as a bolt or a pin, and the valve member 132 may be positioned and held axially between the valve stop 133 and the valve plate 130.
  • the valve member 132 is displaceable between open and closed positions.
  • the biasing member 134 may bias the valve plate 130, the valve member 132, and the valve stop 133 toward the end plate 74 of the movable scroll member 62 to hold them together.
  • the biasing member 134 may take a variety of forms including, but not limited to, a coil spring, a crescent-shaped washer spring, or a wave washer spring.
  • the valve member 132 may include a U-shaped body 136 that defines an aperture 138.
  • the annular body 136 may be aligned with the first and second bypass ports 90a, 90b in a radial position, and the orifice 138 may be aligned with the discharge port 88 in a radial position.
  • the annular body 136 When in the closed position, the annular body 136 may be sealingly engaged with the top surface of the valve plate 130 to seal the orifices of the valve plate 130 communicating with the first and second bypass ports 90a, 90b to disconnect the bypass port 90a. , 90b are in communication with the exhaust passage 20.
  • the exhaust port 88 may communicate with the exhaust passage 20 through a corresponding orifice in the valve plate 130 and an orifice 138 in the valve member 132.
  • the annular body 136 of the valve member 132 may be axially offset upwardly against the valve stop 133, thereby providing communication between the first and second bypass ports 90a, 90b and the exhaust passage 20.
  • both the discharge port 88 and the bypass port 90 can discharge the compressed working fluid.
  • the U-shaped configuration of the valve member 132 helps reduce the number of parts, but the present disclosure is not limited thereto, and the bypass valves 13 may be separately provided for sealing the first bypass port 90a and the second bypass port 90b, respectively.
  • bypass valves and bypass passages can also be provided to selectively communicate intermediate cavities at different pressures.
  • the bypass valve 13 can be opened unidirectionally upward.
  • the bypass valve 13 is closed.
  • the valve assembly may further include a check valve (not shown) provided at the orifice 39 of the partition plate 37 to set the discharge pressure of the exhaust passage 20 and then the discharge port 88 and the bypass port 90 Is the system pressure outside the main valve (ie, the condenser inlet pressure of the system in which the compressor 1 is provided). Therefore, the maximum pressure of the exhaust passage 20 is determined by the system pressure outside the main valve.
  • a check valve (not shown) provided at the orifice 39 of the partition plate 37 to set the discharge pressure of the exhaust passage 20 and then the discharge port 88 and the bypass port 90 Is the system pressure outside the main valve (ie, the condenser inlet pressure of the system in which the compressor 1 is provided). Therefore, the maximum pressure of the exhaust passage 20 is determined by the system pressure outside the main valve.
  • the compressor 10 can provide a larger volume ratio or pressure ratio (that is, a larger discharge pressure), but the system requires a smaller volume ratio or pressure (that is, a lower system pressure), if the compression mechanism completely compresses the working medium And discharged at the discharge port 88, the working fluid will be excessively compressed and then partially expanded, causing a certain loss of efficiency.
  • the bypass passage 91 when the working fluid is compressed halfway, the pressure of the corresponding intermediate cavity at one or more bypass valves 13 may have reached the discharge requirement, that is, the system pressure is reached.
  • the corresponding bypass valve 13 and the main valve can be opened, and the working fluid is discharged in advance without excessive compression.
  • the compression mechanism provides the system with a working medium having a pressure equal to or higher than the pressure of the discharge cavity in an adaptive manner.
  • the bypass path should be set as far as possible outside.
  • the bypass port 90 can only be provided in the first area 84 surrounded by the first annular wall 80 together with the discharge port 88 and the space for the bypass valve 13 needs to be set aside, the bypass port 90 is in the first area
  • the setting range in 84 is greatly restricted, which makes the direct-up and direct-down bypass passages not set on the outside, which results in very limited adjustment capacity of the design volume ratio and design freedom of the bypass valve itself.
  • the bypass passage may be provided to include an upper section and a lower section that are offset from each other in a radial direction, so that the radial position with respect to the bypass port can be less than ⁇ d
  • the radial position where the bypass passage communicates with the compression cavity is adjusted within the range of, where d is the diameter of the bypass passage.
  • FIG. 3a shows a group (for example, three) including side sections of an upper section and a lower section that are offset from each other in a radial direction.
  • FIG. 3 b is a schematic longitudinal sectional view of a fixed scroll member to which the bypass passage shown in FIG. 3 a is applied, and only one of the bypass passages is visible in the sectional view of FIG. 3 b.
  • FIG. 3a in addition to the bypass path 91 ', other components are omitted from the figure.
  • each of the bypass passages 91 extends perpendicularly to the end plate 74 of the fixed scroll member 62 as a whole. It can be seen from the figure that each of the bypass passages 91 'includes an upper section 95' leading to the exhaust passage 20 and a lower section 97 'leading to the middle cavity.
  • the working fluid flows from the middle cavity into the lower section 97 ′ along the arrow in FIG. 3 a, flows into the upper section 95 ′ through the combination of the lower section 97 ′ and the upper section 95 ′, and finally flows into the exhaust gas through the bypass port 90 Channel 20.
  • the lower section 97 ' is biased outward in the radial direction relative to the upper section 95', so that the bypass passage 91 'can communicate with the outer middle compression cavity as far as possible, thereby expanding the volume ratio range of the compressor downward.
  • this communication position can only be adjusted in the radial direction on the order of only a few millimeters.
  • FIGS. 4a-4b, 5 and 6 The configuration of the bypass path 91 according to another embodiment of the present disclosure is described below with reference to FIGS. 4a-4b, 5 and 6. Similar to FIG. 3a, other components are omitted in FIG. 4a, and only a perspective view of a set of (three) bypass passages 91 in this embodiment is shown, and FIG. 4b is a diagram of the bypass passage 91 shown in FIG. 4a applied A schematic longitudinal sectional view of the fixed scroll member 62.
  • FIG. 5 is a partial cross-sectional perspective view of the fixed scroll member 62 shown in FIG. 4b
  • FIG. 6 is a fixed scroll member 62 shown in FIG. 4b at the intermediate connection section 99. Cross-sectional view.
  • the bypass passage 91 includes an end plate 74 that extends substantially perpendicularly (ie, can be completely perpendicular or slightly inclined) to the fixed scroll member 62 to extend to
  • the upper section 95 of the exhaust passage 20 the lower section 97 extending substantially perpendicular to the end plate 74 leading to the intermediate cavity, and the extension of the upper section 95 and the lower section 97 extending substantially parallel to the plane of the end plate 74 Lateral connection section 99.
  • FIG. 4b only the lower section 97 of one of the bypass passages is visible. The working fluid flows from the middle cavity into the lower section 97 along the arrow in FIG.
  • the opening position of the lower section 97 is no longer limited by the opening position of the upper section 95, but can be set on the radially outer side of the first region 84 away from the vertical range of the first region 84 as required. And it communicates with the outer cavity of the scroll mechanism with a lower pressure in the middle cavity, so that the variation range of the variable volume ratio of the compressor 10 can be widened downward in a desired manner, and the overall efficiency of the system is improved.
  • the middle The connection of the connecting section 99 to the upper section 95 and the lower section 97 is smoother and the exhaust is smoother, and this allows the size of the lower section 97 to be increased, thereby further improving the bypass efficiency and the variable volume ratio of the compressor 10 Efficiency and help reduce noise.
  • the opening position of the upper section 95 can also be arbitrarily adjusted in the first region 84, thereby enabling the design of the bypass valve 13 to be More convenient and diverse.
  • the strength of the fixed scroll member 62 is considered
  • the size of the transverse connection section 99 cannot be set too large, so a transverse connection section 99 often cannot meet the design requirements of the opening position of the upper section 95.
  • two cross-connected connection sections are used. In combination, one of the connecting sections projects into a suitable position within the first region 84 for setting the upper section 95. As shown in FIG. 5, in the case where there are two sets of bypass paths, that is, one set of three first bypass paths 91a and one set of three second bypass paths 91b, four can be opened as needed.
  • the other connection section may not directly communicate with the lower section or only communicate with one of the lower sections, so the orientation of the other connection section may be adjusted to an appropriate position as needed for setting thereon Upper section.
  • one connecting section 99b1 is directly communicated with the middle lower section, A connecting section 99a1 is in direct communication with the lower section on the inside.
  • the number of the connecting sections is related to the number of bypass passages and the setting position, and more or fewer intermediate connecting sections may be provided as required.
  • the orientation of the connecting section can be adjusted as required, so only one connecting section can be provided on each side instead of the two connecting sections that are cross-connected.
  • even more connecting sections may be required to realize these bypass passages.
  • the opening position of the upper section can be arbitrarily adjusted by appropriate setting of the connecting section, it is allowed to exhaust the lower sections of the two sets of bypass passages provided on both sides by means of the connecting section. Guided to one location for discharge, that is, allowing only one upper section and one bypass port to bypass the intermediate cavity on both sides. This arrangement can obviously save the design space of the first area 84.
  • the number of bypass passages 91a, 91a, 91b, and 91b on both sides is two, and the two sets of bypass passages 91a, 91a, 91b, and 91b on both sides share one.
  • the connecting section 99b can be oriented to extend toward the common upper section 95 and communicate to the same upper section 95.
  • the number of bypass passages per group is two and one connection section is adopted, the present disclosure is not limited thereto, and the number of bypass passages per group may be one or more than two And more than one connection section may be used, as long as the connection sections directly communicating with the upper section are arranged to lead to a common upper section.
  • a control port can be provided at the discharge port 88.
  • a one-way discharge valve (HVE) of exhaust pressure, and the discharge valve may be provided separately from a single bypass valve or integrated as shown in FIG. 8.
  • the functions of the bypass valve and the discharge valve can be realized simultaneously through the specially designed valve 113, which simplifies the structure and further improves the efficiency of the scroll compressor and the system, which not only improves The efficiency in the over-compressed state also improves the efficiency in the under-compressed state. Similar to the bypass valve 13 shown in FIG. 2, the check valve 113 in FIG.
  • valve 8 also includes a valve plate 130, a valve member 132, a valve stop 133, and a biasing member 134.
  • the sheet-shaped body of the valve member 132 may include aligned with the discharge port 88 and the bypass port 90 in a radial position and cover the valve plate 130 and the discharge port, respectively. 88 and the two parts of the orifice corresponding to the bypass port 90, the valve member 132 itself does not include the orifice 138 (see FIG. 2).
  • both the bypass valve and the discharge valve can be closed, and the scroll compressor continues to compress until the pressure in the discharge cavity is higher than the system pressure above the discharge valve to open the discharge valve; when in the over-compressed state, pass The pressure in the intermediate cavity connected by the bypass passage is higher than the system pressure above the bypass valve. Both the bypass valve and the discharge valve can be opened, and the compressor operates at a low volume ratio.
  • the one-way valves described above only allow the working fluid to flow out unidirectionally from the compression cavity, which can generally prevent the backflow of compressed gas or prevent the compressor from reversing after shutdown.
  • these check valves can be any suitable type of check valves, such as valve discs, spring-loaded check valves and the like.
  • bypass path of the present disclosure is not limited to the configuration of the bypass path shown in the figure, and the bypass path is designed so that the position of the bypass port deviates from the bypass path in the radial direction. All modifications of the location communicating to the intermediate cavity fall within the scope of the present disclosure.
  • the bypass passage instead of a segmented bypass passage that is straight up and down, the bypass passage can be extended obliquely or curvedly compared to the vertical or horizontal direction.
  • the bypass passage composed of a plurality of sections in the embodiment shown in the figure may also be configured to include an upper section, a lower section, and / Or connecting sections. Therefore, unless expressly stated otherwise, "longitudinal" or “lateral” herein cannot be interpreted as a vertical or horizontal direction in the strict sense.
  • the two sets of bypass passages are shown as being disposed substantially symmetrically with respect to the longitudinal axis of the end plate of the fixed scroll member, the present disclosure is not limited thereto and does not affect the compression mechanism
  • two sets of bypass paths can be set accordingly according to whether the design of the compression mechanism is symmetrical, and the configuration and number of the two sets of bypass paths can be different from each other.
  • connection section is provided inside the solid end plate of the fixed scroll component, due to the limitation of the processing method, the transverse connection section is made by punching from the circumferential side surface of the end plate and extending to the Formed at the ends where the upper sections communicate. This means that the actual length of the intermediate connection section exceeds its required length. Because a longer connecting section is used to connect the lower section and the upper section of the bypass passage, the bypass passage is longer. After the system pressure is increased and the bypass valve is closed, the long bypass path will cause the clearance volume of the scroll component to be too large, which will cause the compressor efficiency to decrease.
  • a specially designed threaded hole is used to cooperate with a plug method to prevent the compression working medium from entering the ineffective volume (that is, the ineffective VVR volume) from the effective volume of the bypass passage (that is, the effective VVR volume section) Section), which can greatly reduce the clearance volume, improve the efficiency of the compression mechanism, and also reduce the impact of the lateral process holes on the strength of the scroll component.
  • FIGS. 9a-9c and FIGS. 10a-10c Two embodiments of a bypass passage including a connection section to which a plug is installed according to the present disclosure are described below with reference to FIGS. 9a-9c and FIGS. 10a-10c.
  • 9a is a cross-sectional view of a plug 103 according to an embodiment of the present disclosure
  • FIG. 9b is a partially cut-away perspective view of the bypass passages 91a and 91b installed with the plug 103 of FIG. 9a
  • FIG. 9c is a view shown in FIG. 9b
  • 10a is a cross-sectional view of a plug 203 according to another embodiment of the present disclosure
  • FIG. 10b is a partially cut-away perspective view of the bypass passages 91a and 91b installed with the plug 203 of FIG. 10a, and FIG. Sectional views of the bypass passages 91a and 91b. Among them, for the sake of clarity, in addition to the bypass path, other components are omitted in the figure.
  • the plug 103 has a short stud shape, and a tool engaging groove 105 is formed on one end surface of the plug 103, as shown in Fig. 9a.
  • An internal thread is formed on the inner surface of the lateral process hole forming the connection sections 99a and 99b, and the internal thread extends from the position of the lateral process hole on the circumferential side surface of the end plate to the lateral process hole.
  • a communication position communicating with the lower section that is, over the entire longitudinal length of the dead volume of the transverse process hole.
  • the ineffective volume is formed as a threaded hole
  • a tool such as a screwdriver is used to engage the tool engagement groove 105 on the plug 103 and the plug 103 is screwed into the screw hole and fixed
  • the ineffective volume is isolated from the effective volume at a portion where the ineffective volume is adjacent to the effective volume.
  • the compressed working fluid entering the connection section from the lower section is blocked by the plug 103 and cannot enter the ineffective volume, and can only enter the upper section along the effective connection section (the effective volume of the present disclosure) and be discharged from the bypass port. .
  • the plug 203 has a long stepped column shape and includes a first cylindrical portion 206 and a second cylindrical portion 207.
  • the length of the first cylindrical portion 206 is much shorter than that of the second cylindrical portion.
  • the first cylindrical portion 206 is formed in a stud shape with external threads similar to the plug 103 shown in FIG. 9a for engaging an internal thread formed in a lateral process hole, and the first cylindrical portion 206 has a tool engaging groove 205 formed on an end surface opposite to an end surface connecting the second cylindrical portion 207 for engaging a tool such as a screwdriver.
  • the diameter of the second cylindrical portion 207 is slightly smaller than the diameter of the first cylindrical portion 206, and more specifically slightly smaller than the inner diameter of the connecting section. Unlike the first cylindrical portion 206, the outer peripheral surface of the second cylindrical portion 207 is smooth without threads. Accordingly, the lateral process holes for forming the connecting sections 99a and 99b are formed with internal threads having a length corresponding to the length of the first cylindrical portion 206 only at the positions of the openings on the circumferential side surface of the end plate.
  • the length of the second cylindrical portion 207 can be flexibly determined according to the difference between the length of the invalid volume and the length of the first cylindrical portion 206 to minimize the residual clearance volume.
  • both the former embodiment in which the short plug is matched with the long threaded hole and the latter embodiment in which the short screw hole is matched with the long plug can achieve the purpose of substantially eliminating the clearance volume and thereby improving the efficiency of the compression mechanism. You can choose flexibly according to the situation.
  • the two embodiments, especially the embodiment using a long plug are extremely advantageous for increasing the strength of the fixed scroll component.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

一种涡旋压缩机，其可包括第一涡旋部件（62）和第二涡旋部件（60），第一涡旋部件（62）的第一涡旋叶片（78）与第二涡旋部件（60）的第二涡旋叶片（66）啮合而形成包括吸入腔穴、多个中间腔穴和排放腔穴的一系列压缩腔穴，旁通通路（91）延伸穿过第一涡旋部件（62）的第一端板（74）。旁通通路（91）的一端经由旁通端口（90）与排气通道连通且另一端与中间腔穴连通，旁通端口（90）的位置在径向方向上偏离旁通通路（91）连通至中间腔穴的位置。该旁通通路（91）的构型允许提高涡旋压缩机的可变容积比设计的自由度。

Description

涡旋压缩机
本申请要求于2018年9月19日提交中国国家知识产权局、申请号为201811096406.9、名称为“涡旋压缩机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本公开涉及涡旋压缩机技术领域，更具体地，涉及具有可变容积比的涡旋压缩机。
背景技术
本部分提供了与本公开相关的背景信息，这些信息并不必然是现有技术。
气候控制系统——例如热泵系统、制冷系统或空调系统——可以包括这样的流体回路，该流体回路具有室外热交换器、室内热交换器、设置在室内热交换器与室外热交换器之间的膨胀装置、以及使工作流体(例如，制冷剂)在室内热交换器与室外热交换器之间循环的一个或更多个压缩机。期望压缩机的有效且可靠的操作以确保安装有压缩机的气候控制系统能够根据需要有效且高效地提供冷却效果和/或加热效果。具有可变容积比(VVR)的涡旋压缩机常用于此类系统中以使压缩机的压比与系统所需的工作压力匹配，避免过压缩。
已知的是，涡旋压缩机属于典型的容积式压缩机。涡旋压缩机的压缩机构通常包括定涡旋部件和动涡旋部件，定涡旋部件和动涡旋部件的涡旋叶片之间彼此配合而形成一系列压缩腔穴从而对工质(也称为工作流体，比如气态制冷剂)进行压缩，并且压缩后的高压气体经由排放通路排出到排气通道进而排气压力区。
为了实现可变容积比，在定涡旋部件的端板上设置有连通中间压缩腔穴与排气通道的旁通通路，旁通通路在与排气通道连通的出口处均设置有单向阀(旁通阀)，排气通道和排气压力区的压力即对应于系统的工作压力。当系统所需的工作压力较低时，中间腔穴的压力足以将单向阀打开，将尚未得到充分压缩的中压气体排放到排气压力区，压缩机以低容积比运行；当系统所需的工作压力较高，旁通阀保持关闭状态，压缩机以高容积比运行。
但是由于排气通道所在区域的面积有限，在排放通路和旁通通路的出口进而旁通阀都布置在排气通道有限的空间范围内时，旁通通路的设计自由度很低。不但限制了设计容积比的调整能力，也限制了旁通阀本身的设计。另外， 旁通通路的轴向延伸的中压气体入口需要与轴向延伸的中压气体出口连通，因此中压气体入口的设置位置也受到限制，这也限制了设计容积比的调整能力。
发明内容
在本部分中提供本公开的总概要，而不是本公开的完全范围或本公开所有特征的全面公开。
本公开的一个目的在于提供一种能够避免过压缩导致的系统效率损失的可变容积比涡旋压缩机。
本公开的另一个目的在于提供一种具有高可变容积比设计自由度、特别是容积比设计范围更广的涡旋压缩机，以提高包括该压缩机的系统的运行效率。
根据本公开的一个方面，提供了一种涡旋压缩机，其包括：第一涡旋部件，所述第一涡旋部件包括第一端板和从所述第一端板延伸的第一涡旋叶片；第二涡旋部件，所述第二涡旋部件包括第二端板和从所述第二端板延伸的第二涡旋叶片，所述第二涡旋叶片与所述第一涡旋叶片啮合而形成一系列压缩腔穴，所述一系列压缩腔穴包括吸入腔穴、多个中间腔穴和排放腔穴。所述第一端板包括延伸穿过所述第一端板的旁通通路，所述旁通通路的一端经由旁通端口与排气通道连通且另一端与所述中间腔穴连通，所述旁通端口的位置在径向方向上偏离所述旁通通路连通至所述中间腔穴的位置。
在一些实施方式中，所述旁通通路可以包括彼此连通的第一部段和第二部段，所述第一部段通往所述中间腔穴，所述第二部段通往所述排气通道。
在一些实施方式中，所述旁通通路还可以包括连接所述第一部段和所述第二部段的横向延伸的连接部段。
在一些实施方式中，所述第一端板在与所述第一涡旋叶片相反的一侧可以包括围绕第一区域的第一环形壁，所述第一环形壁限定所述排气通道。所述第一端板还可以包括延伸穿过所述第一端板的排放通路，所述排放通路的一端经由排放端口与所述排气通道连通且另一端与所述排放腔穴连通。所述排放端口和所述旁通端口都设置在所述第一区域内。
在一些实施方式中，在所述旁通端口处可以设置有旁通阀，所述旁通阀为单向阀。
在一些实施方式中，所述旁通通路可以包括第一组旁通通路和第二组旁通通路，所述第一组旁通通路包括一个或多个第一旁通通路，所述第二组旁通通 路包括一个或多个第二旁通通路。
在一些实施方式中，在所述第一组旁通通路中，所述第一部段为一个或多个，所述第二部段为一个或多个，所述第一部段和所述第二部段可以通过一个所述连接部段直接连通。在所述第二组旁通通路中，所述第一部段为一个或多个，所述第二部段为一个或多个，所述第一部段和所述第二部段可以通过一个所述连接部段直接连通。
在一些实施方式中，所述第一组旁通通路包括多个第一旁通通路，在所述多个第一旁通通路中，所述连接部段可以包括第一连接部段和第二连接部段，所述第一连接部段与部分或全部的所述第一部段直接连通，所述第二连接部段与其余的所述第一部段、所述第一连接部段以及所述第二部段直接连通。所述第二组旁通通路包括多个第二旁通通路，在所述多个第二旁通通路中，所述连接部段可以包括第一连接部段和第二连接部段，所述第一连接部段与部分或全部的所述第一部段直接连通，所述第二连接部段与其余的所述第一部段、所述第一连接部段以及所述第二部段直接连通。
在一些实施方式中，所述一个或多个第一旁通通路可以包括相应的一个或多个所述第二部段，并且所述一个或多个第二旁通通路可以包括相应的一个或多个所述第二部段。
在一些实施方式中，所述一个或多个第一旁通通路可以共用一个第二部段，并且所述一个或多个第二旁通通路可以共用一个所述第二部段。
在一些实施方式中，所述一个或多个第一旁通通路和所述一个或多个第二旁通通路可以共用一个所述第二部段和一个所述旁通端口。
在一些实施方式中，在所述排放端口处可以设置有排放阀并且在所述旁通端口处可以设置有旁通阀，所述排放阀和所述旁通阀为单向阀。
在一些实施方式中，所述旁通阀可以与所述排放阀单独设置。或者，所述旁通阀可以与所述排放阀设置成集成阀，在该集成阀中，阀板、阀构件、阀挡和偏压构件中的至少一者为共用构件。
在一些实施方式中，所述第一部段可以在径向方向上远离所述第二部段设置在所述第一区域的径向外侧。
在一些实施方式中，所述连接部段可以包括有效容积区段和无效容积区段，所述无效容积区段从所述连接部段的开孔位置延伸至与其他部段相连通的 连通位置，所述涡旋压缩机还可以包括用于消除所述无效容积区段的堵头。
在一些实施方式中，所述堵头的一个端面可以包括工具接合凹槽，用于与工具接合以将所述堵头插入到所述无效容积区段中。
在一些实施方式中，所述连接部段可以在所述无效容积区段的整个长度上包括内螺纹，所述堵头呈带有外螺纹的螺柱形状，所述堵头的长度小于所述无效容积区段的长度，能够通过将所述堵头旋拧到所述无效容积区段中并固定在所述无效容积区段与所述有效容积区段邻接的部位处而将所述无效容积区段与所述有效容积区段隔离。
在一些实施方式中，所述连接部段可以仅在其开孔位置处形成有内螺纹，所述堵头呈阶梯柱的形状并且包括第一圆柱部分和直径略小于所述第一圆柱部分的第二圆柱部分，所述第一圆柱部分的外周表面上形成有用于与所述内螺纹接合的外螺纹，所述第二部分的长度设定成能够填充所述无效容积区段。
在一些实施方式中，所述第一端板在所述第一环形壁的径向外侧还可以包括第二环形壁，所述第一环形壁与所述第二环形壁之间限定背压室，并且所述背压室经由延伸穿过所述第一端板的背压通路与其中一个所述中间腔穴连通，与所述背压通路连通的中间腔穴不同于与所述旁通通路连通的中间腔穴。
在一些实施方式中，所述排气通道可以经由单向阀与所述涡旋压缩机的排气压力区连通。
根据本公开的具有可变容积比的涡旋压缩机通过改进的增加中间横向部段的旁通通路的设计使得能够提高可变容积比性能并显著提升包含压缩机的整个系统的效率。同时，根据本公开的涡旋压缩机能够在不增大压缩机尺寸的情况下提高旁通通路的大小、形状和位置等的设计自由度，进而提高容积比的调整能力以及旁通阀本身的设计自由度，由此可以更方面地设计旁通通路的排气策略并且可适应多种旁通阀的设计要求。这些都将大大提高压缩机的能效和适用性，具有广泛的应用前景。
附图说明
此处描述的附图是仅出于说明的目的，而并非意在以任何方式限制本公开的范围。
图1是具有可变容积比的示例压缩机的示意性纵向剖视图；
图2是示出了图1所示的压缩机的定涡旋部件和旁通阀的局部剖视立体分 解图；
图3a是根据本公开一实施方式的旁通通路的立体图，图3b是应用了图3a中示出的旁通通路的定涡旋部件的示意性纵向剖视图；
图4a是根据本公开另一实施方式的旁通通路的立体图，图4b是应用了图4a中示出的旁通通路的定涡旋部件的示意性纵向剖视图；
图5是图4b所示的定涡旋部件的局部剖视立体图；
图6是图4b所示的定涡旋部件在中间连接部段处的横向剖视图；
图7是根据本公开另一实施方式的定涡旋部件在中间连接部段处的横向剖视图；
图8是类似于图2的、根据本公开另一实施方式的压缩机构的定涡旋部件的立体图；
图9a是根据本公开一实施方式的堵头的截面图，图9b是连接部段安装有图9a的堵头的旁通通路的局部剖开的立体图，图9c是图9b所示的旁通通路的截面图；以及
图10a是根据本公开另一实施方式的堵头的截面图，图10b是连接部段安装有图10a的堵头的旁通通路的局部剖开的立体图，图10c是图10b所示的旁通通路的截面图。
具体实施方式
以下的描述在本质上只是示例性的而非意在限制本公开及其应用或用途。应当理解的是，附图中对应的附图标记始终指示相同的或对应的部件和特征。本教示适于结合在许多不同类型的立式或卧式涡旋压缩机中，包括密封式机器、敞开驱动式机器和非密封式机器。出于示例的目的，压缩机10被示出为低压侧全封闭立式涡旋压缩机，即，其中马达在密封外壳中由吸气进行冷却，正如在图1的竖向截面中示出的。但是，本教示同样适于结合在高压侧压缩机和卧式压缩机中。
提供示例实施方式以使得本发明公开充分并且向本领域技术人员完整传达了范围。阐述了许多特定细节，例如特定部件、装置、以及方法的示例，以提供对本公开的实施方式的全面的理解。对于本领域技术人员而言将显而易见的是，不必采用特定细节，可以以许多不同的形式实施示例实施方式，并且都不应当解释为对本公开的范围的限制。在一些示例实施方式中，不详细描述公 知方法、公知装置结构以及公知技术。
当元件或层被指处于另一元件或层“上”，或“接合于”、“连接于”或“联接于”另一元件或层时，该元件或层可直接位于该另一元件或层上，或直接接合于、连接于或联接于该另一元件或层，或者可存在居间的元件或层。相反，当元件被指“直接位于”另一元件或层“上”，或“直接接合于”、“直接连接于”或“直接联接于”另一元件或层时，不存在居间的元件或层。用于描述元件之间的关系的其它词语应该以同样的方式进行解释(例如，“位于…之间”对“直接位于…之间”，“邻近于”对“直接邻近于”，等)。如本文所使用的，术语“和/或”包括相关联的所列物品中的一个或多个的任一及全部组合。
尽管本文会使用术语第一、第二、第三等来描述不同的元件、部件、区域、层和/或部分，但这些元件、部件、区域、层和/或部分不应被这些术语所限制。这些术语可以仅用于将一个元件、部件、区域、层和/或部分与另一个区域、层和/或部分进行区分。诸如“第一”、“第二”和其它数字术语之类的术语在本文中使用时并不意味着次序或序列，除非通过上下文清楚地表明。由此，下面所讨论的第一元件、部件、区域、层或部分可被称为第二元件、部件、区域、层或部分，而不脱离示例性实施方式的教示。
参见图1，压缩机10可以包括壳体、制冷剂排放接头14、吸气入口接头(未示出)、马达组件、轴承座组件、压缩机构、保持组件、密封组件和阀组件。
壳体可以容纳马达组件、轴承座组件和压缩机构。壳体可包括：具有吸气入口(未示出)的纵向延伸的外壳30；具有排气出口36的端盖34；横向延伸的隔板37；和底座38。端盖34可固定于外壳30的上端。底座38可固定于外壳30的下端。端盖34和隔板37可大体限定出排气压力区，隔板37、外壳30和底座38可大体限定出吸气压力区。马达组件、轴承座组件和压缩机构设置在吸气压力区。隔板37包括孔口39，孔口39提供压缩机构和排气压力区之间的连通。排气压力区可大体形成压缩机10的排放消音器。制冷剂排放接头14可在端盖34中的排气出口36处附接到壳体上。吸气入口接头可在吸气入口处附接到外壳30上。尽管被图示为包括排气压力区，但是应当理解本公开不局限于具有排气压力区的压缩机，而是同样适用于直排式结构。
马达组件大体可包括定子44、转子46和驱动轴48。定子44可压配装到外壳30中，并通过与转子46之间的电磁相互作用而驱动转子46旋转。转子46可压配装在驱动轴48上。驱动轴48通过转子46可旋转地被驱动并通过轴承座组件支承。驱动轴48中形成有润滑油通道50，以将润滑油从形成于底座38处的油池供给到上部的轴承座组件和压缩机构以提供润滑。驱动轴48可包括偏心曲柄销52，该偏心曲柄销52上具有平直部以便与压缩机构传动地接合。轴承座组件可包括固定在外壳30内的下轴承座56和主轴承座54。
压缩机构可通过马达组件驱动，并且可大体包括动涡旋部件60和定涡旋部件62。动涡旋部件60可包括端板64和从端板64的上表面竖向地向上延伸的动涡旋叶片66。定涡旋部件62可包括端板74和从端板74的下表面竖向地向下延伸的定涡旋叶片78。定涡旋叶片78可与动涡旋叶片66啮合，由此形成一系列压缩腔穴。这些压缩腔穴的容积会在压缩机构的整个压缩周期中变化，并且可以包括沿径向方向位于最外侧的吸入腔穴、若干中间腔穴以及位于中央的排放腔穴。
参见图2，定涡旋部件62在端板74的与定涡旋叶片78所在的一侧相反的另一侧可包括第一环形壁80。第一环形壁80包围大致圆形的第一区域84，排放端口88及旁通端口90可以设置在第一区域内。排放端口88可经由排放通路(排气口)89与排放腔穴连通，旁通端口90可经由旁通通路91与中间腔穴连通。第一环形壁80在其径向内侧限定排气通道20，排气通道20选择性地经由排放端口88和排放通路89与排放腔穴连通和经由旁通端口90和旁通通路91与中间腔穴连通。
在如图2所示的实施方式中，旁通端口90被示出为包括相对于中央排放端口88大体对称地形成的三个第一旁通端口90a和三个第二旁通端口90b，以确保压缩机稳定且高效地在低压缩比与高压缩比之间进行切换。第一旁通端口90a经由第一旁通通路91a与一个中间腔穴连通，第二旁通端口90b经由第二旁通通路91b与相反侧的另一个中间腔穴连通，每个旁通端口可以对应一个旁通通路，参见图5。
定涡旋部件62在第一环形壁80的径向外侧还可以设置有第二环形壁82。在第一环形壁80与第二环形壁82之间围出大致环形的第二区域86。背压室93可以设置在沿径向位于第一环形壁80与第二环形壁82之间的第二区域86 中，并且背压室93可以经由背压通路(未示出)与压缩机构的其中一个中间腔穴连通并在背压室93中建立背压。由此，在压缩机构压缩工质的过程中保持定涡旋部件62和动涡旋部件60彼此抵靠，同时与保持组件协作提供涡旋部件的轴向柔性，从而确保压缩机安全可靠的运行。
保持组件大体可包括延伸穿过定涡旋部件62的套筒18和紧固件16。紧固件16可被固定到主轴承座54上。定涡旋部件62可以通过允许定涡旋部件62基于背压室93的背压有限轴向移位的保持组件固定而不能相对于主轴承座54旋转。
密封组件(例如设置在背压室93中的浮动密封组件)用于与第一和第二环形壁80、82以及隔板37密封接合以使背压室93与压缩机10的低压区域和高压区域隔离。
阀组件可包括用于控制旁通端口90的打开和关闭的旁通阀13，旁通阀13为单向阀。图2中示出了旁通阀13的分解图。如图2中所示，旁通阀13可包括阀板130、阀构件132、阀挡133和偏压构件134。阀板130可以定位在旁通端口90的上方，使得排放端口88和旁通端口90经由阀板130上的孔口露出。阀挡133可通过螺栓或销之类的紧固件固定至阀板130，而阀构件132可定位并被轴向地保持在阀挡133和阀板130之间。阀构件132可在打开和闭合位置之间移位。偏压构件134可以将阀板130、阀构件132和阀挡133朝向动涡旋部件62的端板74偏压而使它们保持在一起。偏压构件134可以呈多种形式，这些形式包括且不局限于螺旋形弹簧、月牙形垫圈式弹簧或者波形垫圈式弹簧。
与旁通端口90在两侧的布置相适应，阀构件132可包括U形本体136，所述环形本体136限定出孔口138。环形本体136可在径向位置上与第一和第二旁通端口90a、90b对准，孔口138可在径向位置上与排放端口88对准。当在闭合位置时，环形本体136可与阀板130的顶面密封地接合，以密封阀板130的与第一和第二旁通端口90a、90b连通的孔口以断开旁通端口90a、90b与排气通道20的连通。此时，排放端口88可以通过阀板130中的相应孔口以及阀构件132中的孔口138与排气通道20连通。当在打开位置时，阀构件132的环形本体136可在轴向上向上偏离而抵靠阀挡133，从而提供第一和第二旁通端口90a、90b与排气通道20之间的连通。此时，排放端口88和旁通端口 90均可排放压缩工质。阀构件132的U形构型有助于减少零部件的数目，但是本公开不限于此，可以单独设置分别用于密封第一旁通端口90a和第二旁通端口90b的旁通阀13。能够理解，也可以设置不同数量和位置的旁通阀和旁通通路，以选择性地连通处于不同压力的中间腔穴。当对应的中间腔穴中的压力大于旁通阀13上方的压力(排气通道20中的压力)时，旁通阀13能够单向地朝上打开。而当旁通阀13上方的压力大于所连通的中间腔穴中的压力时，旁通阀13关闭。
阀组件还可以包括设置在隔板37的孔口39处的单向阀作为总阀(图中未示出)，以将排气通道20进而排放端口88和旁通端口90的排出压力设定为总阀外部的系统压力(即，设置有压缩机1的系统的冷凝器入口压力)。由此，排气通道20的最高压力都由总阀外部的系统压力确定。
当压缩机10能够提供较大的容积比或压比(即较大的排出压力)、然而系统需要的容积比或压比较小(即系统压力较小)时，如果压缩机构将工质完全压缩并在排放端口88排出，则工质将被过度压缩然后再部分膨胀，造成一定的效率损失。然而在设置有旁通通路91的情况下，当工质压缩到中途时，某一个或多个旁通阀13处对应的中间腔穴的压力可能已经达到排放要求，即达到系统压力，此时对应的旁通阀13和总阀都可以打开，工质提前排出而无须过度压缩。另一方面，当压缩机10能够提供的容积比或压比相对较小，而系统需要的容积比或压比相对较大时，对应的中间腔穴的压力可能小于系统压力，无法打开旁通阀13。此时，仅排放端口88打开，压力可以在排气通道20中积聚并在高于总阀上方的系统压力的情况下使总阀向上打开。这样，压缩机构以自适应的方式向系统提供压力等于或高于排出腔穴的压力的工质。
由于越靠近外侧压缩腔穴的压力越低，因此要实现大的可变容积比范围，旁通通路要尽量靠外侧设置。但是考虑到旁通端口90只能和排放端口88一起设置在由第一环形壁80所包围的第一区域84中并且需要留出设置旁通阀13的空间，旁通端口90在第一区域84内的设置范围受到很大的限制，进而使得直上直下式旁通通路也无法靠外侧设置，导致设计容积比的调整能力以及旁通阀本身的设计自由度都非常有限。
为此，根据本公开一实施方式，可以将旁通通路设置成包括在径向方向上彼此偏置的上部部段和下部部段，从而能够相对于旁通端口的径向位置在小于 ±d的范围内调整旁通通路与压缩腔穴连通的径向位置，其中d是旁通通路的直径。
下面结合图3a和图3b对该实施方式进行详细说明，其中，图3a为示出了一组(例如，三个)包括在径向方向上彼此偏置的上部部段和下部部段的旁通通路91’的构型的立体图，图3b是应用了图3a中示出的旁通通路的定涡旋部件的示意性纵向剖视图，图3b的剖视图中仅其中一个旁通通路可见。为清楚起见，在图3a中，除旁通通路91’之外，图中隐去了其他部件。旁通通路91’整体上垂直于定涡旋部件62的端板74延伸。从图中可以看出，每个旁通通路91’包括通往排气通道20的上部部段95’和通往中间腔穴的下部部段97’。工质沿图3a中的箭头从中间腔穴流入下部部段97’，经由下部部段97’与上部部段95’的结合部流入上部部段95’，最后经由旁通端口90流入排气通道20。下部部段97’沿径向方向相对于上部部段95’向外侧偏置，以使旁通通路91’能够尽量与靠外侧的中间压缩腔穴连通，从而向下拓宽压缩机的容积比范围。但是，如上文所述，该连通位置只能沿径向方向在通常情况下只有几毫米的数量级上进行调整。
下面参照图4a-4b、图5和图6描述根据本公开另一实施方式的旁通通路91的构型。类似于图3a，图4a中隐去其他部件，仅示出了该实施方式的一组(三个)旁通通路91的立体图，图4b是应用了图4a中示出的旁通通路91的定涡旋部件62的示意性纵向剖视图，图5是图4b所示的定涡旋部件62的局部剖视立体图，图6是图4b所示的定涡旋部件62在中间连接部段99处的横向剖视图。如图所示，和前一实施方式的旁通通路91’不同，旁通通路91包括大体垂直于(即可以完全垂直于或略微地倾斜于)定涡旋部件62的端板74延伸通往排气通道20的上部部段95、大体垂直于端板74延伸通往中间腔穴的下部部段97、以及大体平行于端板74的平面延伸并连接上部部段95和下部部段97的横向连接部段99。在图4b的剖视图中，仅其中一个旁通通路的下部部段97可见。工质沿图4a中的箭头从中间腔穴流入下部部段97，经由中间连接部段99流入上部部段95，最后经由排放端口88流入排气通道20。由此，使得下部部段97的开孔位置不再受上部部段95的开孔位置的限制，而是可以根据需要远离第一区域84的竖向范围设置在第一区域84的径向外侧而与涡旋机构的更靠外侧的具有较低压力的中间腔穴连通，进而使得压缩机10 的可变容积比的变化范围可以以期望的方式向下拓宽，提高系统的整体效率。另外，由于中间连接部段99的尺寸可以大于上部部段95和下部部段97的尺寸并且上部部段95和下部部段97不是交错连通而是可以完全与连接部段99相连通，因此中间连接部段99与上部部段95和下部部段97的连通更顺畅且排气更通畅，并且这样允许增大下部部段97的尺寸，从而进一步提高压缩机10的旁通效率和变容积比效率且有利于降低噪声。再者，除下部部段97的开孔位置的设计自由度更大之外，上部部段95的开孔位置也可以在第一区域84内任意调整，由此使得旁通阀13的设计可以更加方便和多样。
在图4a所示的实施方式中，由于三个旁通通路91沿涡旋叶片的型线(曲线)布置且都设置在第一区域84的径向外侧，考虑到定涡旋部件62的强度，横向连接部段99的尺寸并不能设置得太大，因此一个横向连接部段99往往满足不了上部部段95的开孔位置的设计要求，为此采用了两个交叉连通的连接部段的组合，其中一个连接部段伸入第一区域84内的适当位置，用于设置上部部段95。如图5所示，在存在两组旁通通路——即，三个第一旁通通路91a一组，三个第二旁通通路91b一组——的情况下，可以根据需要开设四个横向连接部段99a1、99a2和99b1、99b2。并且，在每组旁通通路中，可以是三个下部部段或仅其中两个下部部段限定一个连接部段的取向，即，与一个连接部段直接连通。相应地，另一个连接部段可以不与下部部段直接连通或者仅与其中一个下部部段连通，因此该另一个连接部段的取向可以根据需要调整到合适的位置，用于在其上设置上部部段。如图6所示，在两组旁通通路91a和91b的用于设置上部部段95a和95b的两个连接部段99a1和99b1中，一个连接部段99b1与中间的下部部段直接连通，一个连接部段99a1与内侧的下部部段直接连通。
应当指出，连接部段的设置数目与旁通通路的数目和设置位置相关，可以根据需要设置更多或者更少的中间连接部段。例如，在两侧各设置一个旁通通路的情况下，连接部段的取向可以根据需要随意调整，因此可以在每一侧仅设置一个连接部段替代交叉连通的两个连接部段。相反，在每组旁通通路的数目超过三个并且分散布置的情况下，甚至可能需要更多的连接部段用于实现这些旁通通路。另外，如上所述，由于上部部段的开孔位置可以通过连接部段的适当设置任意调整，因此允许借助于连接部段将设置于两侧的两组旁通通路的下 部部段的排气引导至一个位置进行排放，也就是说，允许仅设置一个上部部段和一个旁通端口来旁通两侧的中间腔穴。这种布置显然能够节省第一区域84的设计空间。
例如，参见图7所示的实施方式，两侧的旁通通路91a、91a和91b、91b的数目都是两个，并且两侧的这两组旁通通路91a、91a和91b、91b共用一个上部部段95和一个旁通端口90，为此两组旁通通路分别布置成使得与两个下部部段97a、97a均连通的连接部段99a以及与两个下部部段97b、97b均连通的连接部段99b能够定向成朝向共同的上部部段95延伸并连通至该同一上部部段95。尽管在图7所示的实施方式中，每组旁通通路的数目为两个并且采用一个连接部段，但是本公开不限于此，每组旁通通路的数目可以为一个或多于两个并且可以采用多于一个的连接部段，只要与上部部段直接连通的连接部段布置成通向共同的上部部段即可。
如图8所示，在这种仅设置一个上部部段95和一个旁通端口90的情况下，替代在隔板37的孔口39处设置总阀，可以在排放端口88处设置用于控制排气压力的单向排放阀(HVE)，并且该排放阀可以与单个旁通阀分开设置或者如图8中示出的那样设置成一体。在图8所示的实施方式中，通过特殊设计的阀113，可以同时实现旁通阀和排放阀的功能，这简化了结构，也使涡旋压缩机进而系统的效率进一步提升，不但改善了过压缩状态下的效率，同时也改善了欠压缩状态下的效率。和图2中所示的旁通阀13类似，图8中的单向阀113也包括阀板130、阀构件132、阀挡133和偏压构件134。与排放端口88和旁通端口90的布置相适应，阀构件132的片状本体可包括在径向位置上分别与排放端口88和旁通端口90对准并用于覆盖阀板130上与排放端口88和旁通端口90对应的孔口的两部分，阀构件132本身不包括孔口138(参见图2)。
当处于欠压缩状态时，旁通阀和排放阀可以都关闭，涡旋压缩机持续压缩直至排放腔穴的压力高于排放阀上方的系统压力使得排放阀打开；当处于过压缩状态时，通过旁通通路连通的中间腔穴的压力即已高出旁通阀上方的系统压力，旁通阀和排放阀可以都打开，压缩机以低容积比运行。
上文所述的这些单向阀仅允许工质从压缩腔穴单向地流出，从而可大体防止压缩气体的回流或防止压缩机在关机后反转。并且这些单向阀可以是任意适当类型的单向阀，例如阀片、弹簧式单向阀等。
可以理解的是，本公开的旁通通路的设计理念并不限于图中所示的旁通通路的构型，将旁通通路设计成使得旁通端口的位置在径向方向上偏离旁通通路连通至中间腔穴的位置的所有改型都落在本公开的范围内。例如，替代直上直下的一部段式旁通通路，可以使旁通通路相较于竖直方向或水平方向倾斜延伸或弯曲延伸。类似地，图中所示实施方式中的由多个部段构成的旁通通路也可以构造成包括相较于竖直方向或水平方向成角度地倾斜延伸的上部部段、下部部段和/或连接部段。因此，除非另外明确说明，否则本文中的“纵向”或“横向”不能解释为严格意义上的竖直方向或水平方向。
另外，尽管在上述实施方式中，两组旁通通路被示出为相较于定涡旋部件的端板的纵向轴线大体对称地设置，但是本公开并不局限于此，在不影响压缩机构的正常运行的情况下，可以根据压缩机构的设计是否对称来相应地设置两组旁通通路，并且两组旁通通路的构型和数目可以彼此不同。
应当注意的是，由于连接部段设置在定涡旋部件的实心端板的内部，受加工方法的限制，横向连接部段都是通过从端板的周向侧表面打孔并一直延伸至与上部部段相连通的端部处而形成的。这意味着中间连接部段的实际长度超过了其所需长度。由于采用了较长的连接部段连接旁通通路的下部部段与上部部段，导致旁通通路较长。在系统压力升高使得旁通阀关闭后，长的旁通通路会造成涡旋部件的余隙容积过大，从而导致压缩机效率下降。根据本公开的一种实施方式，通过特殊设计的螺纹孔配合堵头的方法来阻止压缩工质从旁通通路的有效容积(即，有效VVR容积区段)进入无效容积(即，无效VVR容积区段)，从而可以大幅减小余隙容积，提高压缩机构的效率，同时还能够降低横向工艺孔对涡旋部件的强度造成的影响。
下面参照图9a-9c和图10a-10c来描述根据本公开的包括安装有堵头的连接部段的旁通通路的两种实施方式。图9a是根据本公开一实施方式的堵头103的截面图，图9b是安装有图9a的堵头103的旁通通路91a和91b的局部剖开的立体图，图9c是图9b所示的旁通通路91a和91b的截面图。图10a是根据本公开另一实施方式的堵头203的截面图，图10b是安装有图10a的堵头203的旁通通路91a和91b的局部剖开的立体图，图10c是图10b所示的旁通通路91a和91b的截面图。其中，为清楚起见，除旁通通路之外，图中隐去了其他部件。
在图9a至图9c所示的实施方式中，堵头103呈短螺柱形状，并且在堵头103的一个端面上形成有工具接合凹槽105，如图9a中所示。在形成连接部段99a和99b的横向工艺孔的内侧表面上形成有内螺纹，该内螺纹从横向工艺孔的位于端板的周向侧表面上的开孔位置处一直延伸至横向工艺孔的与下部部段相连通的连通位置处，即，在横向工艺孔的无效容积的整个纵向长度上延伸。在旁通通路91a和91b完成打孔并且无效容积形成为螺纹孔之后，采用螺丝刀之类的工具与堵头103上的工具接合凹槽105接合并将堵头103旋拧到螺纹孔中并固定在无效容积与有效容积邻接的部位处而将无效容积与有效容积隔离。由此，从下部部段进入连接部段的压缩工质被堵头103拦截而不能进入无效容积，只能顺着有效连接部段(本公开的有效容积)进入上部部段从旁通端口排出。
在图10a至图10c所示的另一实施方式中，堵头203呈长阶梯柱形状，并且包括第一圆柱部分206和第二圆柱部分207，第一圆柱部分206的长度远小于第二圆柱部分207的长度。如图10a所示，第一圆柱部分206类似于图9a中所示的堵头103形成为带有外螺纹的螺柱形状，用于接合横向工艺孔中形成的内螺纹，并且第一圆柱部分206在与连接第二圆柱部分207的端面相反的端面上形成有工具接合凹槽205，用于接合螺丝刀之类的工具。第二圆柱部分207的直径略小于第一圆柱部分206，更确切地略小于连接部段的内径。和第一圆柱部分206不同，第二圆柱部分207的外周表面是光滑的，不带螺纹。相应地，用于形成连接部段99a和99b的横向工艺孔仅在位于端板的周向侧表面上的开孔位置处形成有长度与第一圆柱部分206的长度对应的内螺纹。安装堵头203时，先将第二圆柱部分207插入横向工艺孔内，最后借助于工具将第一圆柱部分206旋拧到横向工艺孔中与开孔位置处的内螺纹接合并固定。在这种实施方式中，第二圆柱部分207的长度可以根据无效容积的长度与第一圆柱部分206的长度之差来灵活地确定，以尽量减少残留余隙容积。
可以看出，无论是短堵头与长螺纹孔配合的前一实施方式还是短螺纹孔与长堵头配合的后一实施方式都可以实现大体消除余隙容积从而提高压缩机构效率的目的，实践中可以根据情况灵活选用。此外，两种实施方式尤其是采用长堵头的实施方式对于提高定涡旋部件的强度极为有利。
尽管上文已经具体描述了本公开的各种实施方式和变型，但是本领域技术 人员应该理解，本公开并不局限于上述具体的实施方式和变型而是可以包括其他各种可能的组合和结合。在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其他的变型和变体。所有这些变型和变体都落入本公开的范围内。而且，所有在此描述的构件都可以由其他技术性上等同的构件来代替。

Claims (20)

  1. 一种涡旋压缩机，包括：
    第一涡旋部件，所述第一涡旋部件包括第一端板和从所述第一端板延伸的第一涡旋叶片；
    第二涡旋部件，所述第二涡旋部件包括第二端板和从所述第二端板延伸的第二涡旋叶片，所述第二涡旋叶片与所述第一涡旋叶片啮合而形成一系列压缩腔穴，所述一系列压缩腔穴包括吸入腔穴、多个中间腔穴和排放腔穴，
    其中，
    所述第一端板包括延伸穿过所述第一端板的旁通通路，所述旁通通路的一端经由旁通端口与排气通道连通且另一端与所述中间腔穴连通，所述旁通端口的位置在径向方向上偏离所述旁通通路连通至所述中间腔穴的位置。
  2. 如权利要求1所述的涡旋压缩机，其中，所述旁通通路包括彼此连通的第一部段和第二部段，所述第一部段通往所述中间腔穴，所述第二部段通往所述排气通道。
  3. 如权利要求2所述的涡旋压缩机，其中，所述旁通通路还包括连接所述第一部段和所述第二部段的横向延伸的连接部段。
  4. 如权利要求3所述的涡旋压缩机，其中，
    所述第一端板在与所述第一涡旋叶片相反的一侧包括围绕第一区域的第一环形壁，所述第一环形壁限定所述排气通道，
    所述第一端板还包括延伸穿过所述第一端板的排放通路，所述排放通路的一端经由排放端口与所述排气通道连通且另一端与所述排放腔穴连通，并且
    所述排放端口和所述旁通端口都设置在所述第一区域内。
  5. 如权利要求1所述的涡旋压缩机，其中，在所述旁通端口处设置有旁通阀，所述旁通阀为单向阀。
  6. 如权利要求4所述的涡旋压缩机，其中，所述旁通通路包括第一组旁 通通路和第二组旁通通路，所述第一组旁通通路包括一个或多个第一旁通通路，所述第二组旁通通路包括一个或多个第二旁通通路。
  7. 如权利要求6所述的涡旋压缩机，其中，
    在所述第一组旁通通路中，所述第一部段为一个或多个，所述第二部段为一个或多个，所述第一部段和所述第二部段通过一个所述连接部段直接连通，并且
    在所述第二组旁通通路中，所述第一部段为一个或多个，所述第二部段为一个或多个，所述第一部段和所述第二部段通过一个所述连接部段直接连通。
  8. 如权利要求6所述的涡旋压缩机，其中，
    所述第一组旁通通路包括多个第一旁通通路，在所述多个第一旁通通路中，所述连接部段包括第一连接部段和第二连接部段，所述第一连接部段与部分或全部的所述第一部段直接连通，所述第二连接部段与其余的所述第一部段、所述第一连接部段以及所述第二部段直接连通，并且
    所述第二组旁通通路包括多个第二旁通通路，在所述多个第二旁通通路中，所述连接部段包括第一连接部段和第二连接部段，所述第一连接部段与部分或全部的所述第一部段直接连通，所述第二连接部段与其余的所述第一部段、所述第一连接部段以及所述第二部段直接连通。
  9. 如权利要求7或8所述的涡旋压缩机，其中，所述一个或多个第一旁通通路包括相应的一个或多个所述第二部段，并且所述一个或多个第二旁通通路包括相应的一个或多个所述第二部段。
  10. 如权利要求7或8所述的涡旋压缩机，其中，所述一个或多个第一旁通通路共用一个第二部段，并且所述一个或多个第二旁通通路共用一个第二部段。
  11. 如权利要求10所述的涡旋压缩机，其中，所述一个或多个第一旁通通路和所述一个或多个第二旁通通路共用一个所述第二部段和一个所述旁通 端口。
  12. 如权利要求11所述的涡旋压缩机，其中，在所述排放端口处设置有排放阀并且在所述旁通端口处设置有旁通阀，所述排放阀和所述旁通阀为单向阀。
  13. 如权利要求12所述的涡旋压缩机，其中，所述旁通阀与所述排放阀单独设置，或者，所述旁通阀与所述排放阀设置成集成阀，在该集成阀中，阀板、阀构件、阀挡和偏压构件中的至少一者为共用构件。
  14. 如权利要求1至8中的任一项所述的涡旋压缩机，其中，所述第一部段在径向方向上远离所述第二部段设置在所述第一区域的径向外侧。
  15. 如权利要求1至8中的任一项所述的涡旋压缩机，其中，所述连接部段包括有效容积区段和无效容积区段，所述无效容积区段从所述连接部段的开孔位置延伸至与其他部段相连通的连通位置，所述涡旋压缩机还包括用于消除所述无效容积区段的堵头。
  16. 如权利要求15所述的涡旋压缩机，其中，所述堵头的一个端面包括工具接合凹槽，用于与工具接合以将所述堵头插入到所述无效容积区段中。
  17. 如权利要求15所述的涡旋压缩机，其中，所述连接部段在所述无效容积区段的整个长度上包括内螺纹，所述堵头呈带有外螺纹的螺柱形状，所述堵头的长度小于所述无效容积区段的长度，能够通过将所述堵头旋拧到所述无效容积区段中并固定在所述无效容积区段与所述有效容积区段邻接的部位处而将所述无效容积区段与所述有效容积区段隔离。
  18. 如权利要求15所述的涡旋压缩机，其中，所述连接部段仅在其开孔位置处形成有内螺纹，所述堵头呈阶梯柱的形状并且包括第一圆柱部分和直径略小于所述第一圆柱部分的第二圆柱部分，所述第一圆柱部分的外周表面上形 成有用于与所述内螺纹接合的外螺纹，所述第二部分的长度设定成能够填充所述无效容积区段。
  19. 如权利要求1至8中的任一项所述的涡旋压缩机，其中，所述第一端板在所述第一环形壁的径向外侧还包括第二环形壁，所述第一环形壁与所述第二环形壁之间限定背压室，并且所述背压室经由延伸穿过所述第一端板的背压通路与其中一个所述中间腔穴连通，与所述背压通路连通的中间腔穴不同于与所述旁通通路连通的中间腔穴。
  20. 如权利要求1至8中的任一项所述的涡旋压缩机，其中，所述排气通道经由单向阀与所述涡旋压缩机的排气压力区连通。
PCT/CN2019/106376 2018-09-19 2019-09-18 涡旋压缩机 WO2020057535A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201811096406 2018-09-19
CN201811096406.9 2018-09-19

Publications (1)

Publication Number Publication Date
WO2020057535A1 true WO2020057535A1 (zh) 2020-03-26

Family

ID=69848769

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/106376 WO2020057535A1 (zh) 2018-09-19 2019-09-18 涡旋压缩机

Country Status (2)

Country Link
CN (2) CN211343341U (zh)
WO (1) WO2020057535A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN211343341U (zh) * 2018-09-19 2020-08-25 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0979152A (ja) * 1995-09-11 1997-03-25 Sanyo Electric Co Ltd スクロール圧縮機
CN1272906A (zh) * 1998-06-12 2000-11-08 大金工业株式会社 多级容量控制涡旋压缩机
CN1301923A (zh) * 1999-12-24 2001-07-04 Lg电子株式会社 非对称涡旋压缩机
KR100332796B1 (ko) * 2000-01-11 2002-04-18 구자홍 스크롤 압축기
US6379123B1 (en) * 1997-05-12 2002-04-30 Matsushita Electric Industrial Co., Ltd. Capacity control scroll compressor
CN102086865A (zh) * 2009-12-08 2011-06-08 丹佛斯涡旋技术有限责任公司 电磁与流体混合控制的涡旋压缩机容量调节
CN106460842A (zh) * 2014-06-03 2017-02-22 艾默生环境优化技术有限公司 可变容积比涡旋压缩机
US9920759B2 (en) * 2014-01-06 2018-03-20 Lg Electronics Inc. Scroll compressor with back pressure device

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07293456A (ja) * 1994-04-28 1995-11-07 Sanyo Electric Co Ltd スクロール圧縮機
US5678985A (en) * 1995-12-19 1997-10-21 Copeland Corporation Scroll machine with capacity modulation
KR101576459B1 (ko) * 2009-02-25 2015-12-10 엘지전자 주식회사 스크롤 압축기 및 이를 적용한 냉동기기
CN102042224B (zh) * 2009-10-14 2014-03-19 松下电器产业株式会社 涡旋式压缩机
US8517703B2 (en) * 2010-02-23 2013-08-27 Emerson Climate Technologies, Inc. Compressor including valve assembly
CN105570127B (zh) * 2016-02-16 2018-12-04 珠海格力节能环保制冷技术研究中心有限公司 压缩机及具有其的空调器
CN108240337B (zh) * 2016-12-23 2020-10-09 艾默生环境优化技术(苏州)有限公司 阀组件和涡旋压缩机
JP6606804B2 (ja) * 2016-12-26 2019-11-20 三菱重工サーマルシステムズ株式会社 スクロール圧縮機
CN211343341U (zh) * 2018-09-19 2020-08-25 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0979152A (ja) * 1995-09-11 1997-03-25 Sanyo Electric Co Ltd スクロール圧縮機
US6379123B1 (en) * 1997-05-12 2002-04-30 Matsushita Electric Industrial Co., Ltd. Capacity control scroll compressor
CN1272906A (zh) * 1998-06-12 2000-11-08 大金工业株式会社 多级容量控制涡旋压缩机
CN1301923A (zh) * 1999-12-24 2001-07-04 Lg电子株式会社 非对称涡旋压缩机
KR100332796B1 (ko) * 2000-01-11 2002-04-18 구자홍 스크롤 압축기
CN102086865A (zh) * 2009-12-08 2011-06-08 丹佛斯涡旋技术有限责任公司 电磁与流体混合控制的涡旋压缩机容量调节
US9920759B2 (en) * 2014-01-06 2018-03-20 Lg Electronics Inc. Scroll compressor with back pressure device
CN106460842A (zh) * 2014-06-03 2017-02-22 艾默生环境优化技术有限公司 可变容积比涡旋压缩机

Also Published As

Publication number Publication date
CN211343341U (zh) 2020-08-25
CN110925195A (zh) 2020-03-27

Similar Documents

Publication Publication Date Title
US10962008B2 (en) Variable volume ratio compressor
US11434910B2 (en) Scroll compressor having hub plate
US11022119B2 (en) Variable volume ratio compressor
JP5314326B2 (ja) 冷媒圧縮機
KR101329593B1 (ko) 용량 조절 시스템 또는 유체 주입 시스템을 가지고 있는 압축기
US10378539B2 (en) System including high-side and low-side compressors
US10605251B2 (en) Turbo compressor
US20150345493A1 (en) Variable volume ratio scroll compressor
US7153109B2 (en) Variable capacity rotary compressor
US7059842B2 (en) Variable capacity rotary compressor
CN108361195A (zh) 可变排量涡旋压缩机
WO2020057535A1 (zh) 涡旋压缩机
JP2018009565A (ja) 多段圧縮機
JP3942784B2 (ja) スクロール圧縮機
WO2018003431A1 (ja) 多段圧縮機
US10480513B2 (en) Intermediate discharge port for a compressor
CN110836183A (zh) 压缩机及其压缩机构
KR102697605B1 (ko) 스크롤 압축기
WO2022269752A1 (ja) ロータリ圧縮機および冷凍サイクル装置
WO2021157121A1 (ja) インジェクション機構付き圧縮機
US20240218881A1 (en) Compressor With Shutdown Assembly
JP2015017552A (ja) 気体圧縮機
KR20230129538A (ko) 밀봉 어셈블리를 구비한 압축기
JP2006144622A (ja) 気体圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19862474

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19862474

Country of ref document: EP

Kind code of ref document: A1