WO2020108224A1 - 具有密封-截油结构的涡旋压缩机 - Google Patents

具有密封-截油结构的涡旋压缩机 Download PDF

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Publication number
WO2020108224A1
WO2020108224A1 PCT/CN2019/114652 CN2019114652W WO2020108224A1 WO 2020108224 A1 WO2020108224 A1 WO 2020108224A1 CN 2019114652 W CN2019114652 W CN 2019114652W WO 2020108224 A1 WO2020108224 A1 WO 2020108224A1
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WO
WIPO (PCT)
Prior art keywords
oil
scroll compressor
hole
compressor according
partition
Prior art date
Application number
PCT/CN2019/114652
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English (en)
French (fr)
Inventor
胡小伟
倪凌枫
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
Priority claimed from CN201821990326.3U external-priority patent/CN209180006U/zh
Priority claimed from CN201811443483.7A external-priority patent/CN111237189A/zh
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
Priority to US17/298,473 priority Critical patent/US20220136508A1/en
Publication of WO2020108224A1 publication Critical patent/WO2020108224A1/zh

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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
    • 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
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C29/0092—Removing solid or liquid contaminants from the gas under pumping, e.g. by filtering or deposition; Purging; Scrubbing; Cleaning
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers

Definitions

  • the present application relates to a scroll compressor with a sealed-oil intercepting structure. .
  • Scroll compressors generally include a compression mechanism composed of a fixed scroll member and a movable scroll member.
  • the compression mechanism is used to compress the working fluid from the low-pressure side to a high-pressure state and discharge it into the external circulation line through the exhaust connector on the high-pressure side.
  • the lubricant in the compressor forms droplets or mist due to the movement of various moving parts in the compressor and mixes in the working fluid. These lubricant droplets or mist mixed in the working fluid are sucked from the suction port on the low-pressure side into a series of compression chambers defined by the fixed scroll member and the movable scroll member to function as lubrication, sealing, cooling, etc.
  • the working fluid mixed with lubricant is compressed into a high-pressure state (gaseous mixture) by the scroll assembly, and then enters the external circulation line outside the compressor housing through the exhaust connector on the high-pressure side.
  • a partition that divides the internal space of the compressor into a high-pressure side and a low-pressure side and a corresponding seal assembly are provided inside the compressor.
  • the seal assembly is disposed in the recess on the end plate of the fixed scroll component.
  • the sealing assembly (especially the floating sealing assembly) includes an upper plate, a lower plate, and a seal provided between the upper plate and the lower plate. The top end of the upper plate can abut the collar on the partition or directly under the partition The surface is sealed to achieve effective separation between the high-pressure side and the low-pressure side.
  • An object of the present application is to provide a scroll compressor capable of additionally lubricating and sealing the inside of the scroll.
  • Another object of the present application is to provide a seal-oil intercepting structure for a scroll compressor that can improve the sealing performance of a metal-metal seal between a seal ring and a partition plate.
  • Still another object of the present application is to provide a seal-oil intercepting structure for a scroll compressor that can reduce the wear of the metal-metal sealing surface between the seal ring and the partition plate.
  • Another object of the present application is to provide a scroll compressor that can facilitate the management of compressor lubricating oil.
  • a scroll compressor including: a partition unit having an exhaust hole through which exhaust gas passes and a first sealing surface on the bottom side of the partition unit; and a seal An assembly, the sealing assembly is arranged below the partition unit, and at the top end includes a second sealing surface configured to surround a central hole of the sealing assembly, the second sealing surface abuts against the first sealing surface to form a sealing portion separating the high-pressure side and the low-pressure side
  • the scroll compressor further includes an oil intercepting device, which is provided at the exhaust hole of the partition unit to trap the oil in the exhaust gas and allow the trapped oil to flow back through the partition unit.
  • the separator unit includes a separator that defines an exhaust hole and a wear-resistant gasket disposed on the bottom side of the separator around the exhaust hole, and the bottom surface of the wear-resistant gasket provides a first sealing surface.
  • the partition unit includes a partition having a central hole and an additional device installed in the central hole of the partition, the additional device defines an exhaust hole of the partition unit and a first sealing surface.
  • the additional device is a sealing ring
  • the central opening of the sealing ring defines an exhaust hole of the partition unit
  • the bottom surface of the sealing ring provides a first sealing surface
  • the additional device may include a sealing ring and a cylinder body integrally or separately formed with the sealing ring, the cylinder body extends upward around the central opening of the sealing ring, and the cylinder body is provided with at least one exhaust hole serving as a partition unit The orifice and the bottom surface of the sealing ring provide the first sealing surface.
  • an oil intercepting device is provided in the cylinder body across the inner diameter of the cylinder body to intercept the oil in the exhaust gas to be exhausted through the at least one orifice on the cylinder body.
  • the oil intercepting device integrally surrounds the outside of the cylinder above the seal ring.
  • At least one orifice is provided on the side wall of the barrel.
  • the oil intercepting devices may be separately provided in the at least one orifice on the barrel in a separate form.
  • the top end of the sealing assembly extends radially inward beyond the wall surface of the central channel of the partition unit, and the inner edge of the top end is provided with a protrusion that protrudes upward radially inward of the wall surface of the central channel of the partition unit, wherein, A gap is left between the protrusion and the wall surface of the central passage so as to receive at least a part of oil dripping from the oil intercepting device.
  • At least one oil hole may be provided in the seal ring, the number and position of the oil holes are set to be suitable for receiving oil from the oil intercepting device, and the oil holes are positioned to be located in the radial direction of the seal portion in the assembled state Inside.
  • the oil hole may be a cylindrical through hole, an inverted tapered through hole, or a through hole with a flared portion at the upper end.
  • An oil guide groove may be provided on the seal ring, and the oil guide groove is located above the oil hole for receiving oil dripping from the oil intercepting device and guiding the oil into the oil hole.
  • a groove located between the second sealing surface and the protruding portion may be provided on the top end of the seal assembly.
  • the groove is located below the oil hole in the assembled state to receive oil from the oil hole and the gap.
  • the barrel may be configured as a muffler cover adapted to reduce exhaust noise.
  • the oil intercepting device may be a filtering device with a filter screen.
  • the filtering device may be an integrated filtering device, which can be adapted to be flat, dome-shaped, conical or topped cylindrical according to the arrangement of the exhaust holes of the partition unit; when the partition unit has multiple exhausts In the case of a hole, the filter device may be a separate filter device provided at the exhaust hole of the partition unit, respectively.
  • the oil intercepting device may be a multi-layer textile fiber filter or a multi-layer metal wire filter.
  • the seal assembly may be a floating seal ring assembly provided in a recess at the fixed scroll end plate of the scroll compressor, and the top end is provided by the upper plate of the floating seal ring assembly.
  • a metal-metal seal is provided between the first sealing surface and the second sealing surface.
  • the compressor according to the present application can realize the secondary separation of the lubricating oil/refrigerant mixture after compression, and use the leakage channel to reintroduce the lubricating oil into the interior of the scroll to lubricate and seal the interior of the scroll to improve Rotating performance and reliability.
  • the compressor according to the present application can also allow a part of the trapped oil to be re-introduced into the low-pressure oil sump side through the leakage passage between the metal-metal sealing surfaces due to deformation or relative movement, etc., which can further Improve the stability and compression performance of the compressor operation: on the one hand, the separated lubricating oil is guided to the metal-metal sealing surface between the sealing ring and the separator for oil sealing, thereby improving the sealing performance; on the other hand, it can The guide lubricating oil lubricates the metal-to-metal sealing surface between the seal ring and the separator, thereby reducing wear due to relative motion.
  • Figure 1 is a longitudinal sectional view of a conventional scroll compressor
  • FIG. 2a is a longitudinal cross-sectional view schematically showing the pressure distribution in the scroll compressor shown in FIG. 1;
  • Figure 2b is an exploded view of a double-plate floating seal ring assembly
  • Figure 2c schematically shows the metal-metal seal between the separator and the seal assembly
  • FIG. 3a is a partial cross-sectional view of a scroll compressor according to a first embodiment of the present application
  • Figure 3b is a cross-sectional perspective view of the upper plate of the seal assembly with protrusions
  • FIG. 3c is a partial cross-sectional view of a modified form of the scroll compressor shown in FIG. 3a, which includes the upper plate of the seal assembly shown in FIG. 3b, and the travel path of the lubricating oil in the exhaust gas is marked with arrows;
  • FIG. 4a is a partial cross-sectional view of a scroll compressor according to a second embodiment of the present application.
  • FIG. 4b is a partial cross-sectional view of a modified form of the scroll compressor shown in FIG. 4a, which includes the upper plate of the seal assembly shown in FIG. 3b;
  • FIG. 5a is a perspective view of a noise reduction assembly applied in a third embodiment of the present application.
  • FIG. 5b is a partial cross-sectional view of a scroll compressor according to a third embodiment of the present application.
  • 5c is a perspective cross-sectional view showing another combined form of the separator unit and the filtering device according to the third embodiment of the present application;
  • FIG. 5d is a partial cross-sectional view of the scroll compressor including the partition unit and the filtering device in FIG. 5c;
  • FIG. 5e is a partial cross-sectional view of a modified form of the scroll compressor shown in FIG. 5d, which includes the upper plate of the seal assembly shown in FIG. 3b, and the travel path of the lubricating oil in the exhaust gas is marked with arrows;
  • FIG. 6a is a partial cross-sectional view of a scroll compressor including a seal-oil intercepting structure according to a fourth embodiment of the present application.
  • FIG. 6b is a partial cross-sectional view of a modified form of the scroll compressor shown in FIG. 6a, which includes the upper plate of the seal assembly shown in FIG. 3b.
  • the scroll compressor 100 (hereinafter sometimes also referred to as a compressor) generally includes a housing 110.
  • the housing 110 may include a substantially cylindrical body 111, a top cover 112 provided at the upper end of the body 111, a bottom cover 114 positioned below the body 111, and a top cover 112 and the body 111 to separate the internal space of the compressor
  • the partition 116 is formed into a high-pressure side and a low-pressure side.
  • the space between the partition 116 and the top cover 112 constitutes the high-pressure side HC
  • the space around the scroll assembly below the partition 116 constitutes the low-pressure side LC.
  • An intake joint 118 for sucking fluid is provided on the low-pressure side LC, and an exhaust joint 119 for discharging compressed fluid is provided on the high-pressure side HC.
  • a motor 120 composed of a stator 122 and a rotor 124 is provided in the housing.
  • the rotor 124 is provided with a drive shaft 130 to drive the compression mechanism composed of the fixed scroll member 150 and the movable scroll member 160.
  • the fixed scroll part 150 includes a split ring member 154 provided above the end plate for forming the recess 158.
  • the annular member 154 defines an exhaust passage 152 inside. The space of the exhaust passage 152 also constitutes the high-pressure side HC.
  • a seal assembly (for example, a floating seal ring assembly) S is provided in the concave portion 158 of the fixed scroll member 150. That is, the seal assembly S is provided between the partition 116 and the fixed scroll member 150.
  • the sealing assembly S cooperates with the concave portion 158 to form a back pressure chamber BC that provides back pressure to the fixed scroll member 150.
  • the pressure in the back pressure chamber is lower than the high pressure side but higher than the low pressure side, which is equivalent to the intermediate pressure region MC.
  • the sealing assembly S may include an upper plate S1, a lower plate S2, and a first seal S3 and a second seal S4 disposed between the upper plate S1 and the lower plate S2.
  • the shape of the sealing assembly S substantially corresponds to the shape of the recess 158, so that the first seal S3 can seal against the radial inner side wall of the recess 158, and the second seal S4 can seal against the radial outer side wall of the recess 158 .
  • top end S11 of the upper plate S1 may abut against a wear-resistant element mounted on the partition 116 (for example, the bottom side of a wear-resistant gasket or seal ring as described below) or directly abut the seal portion of the partition 116 to Sealing is achieved to achieve separation between the high-pressure side and the low-pressure side.
  • FIG. 2c shows the metal-metal seal MM between the top end S11 of the upper plate S1 and the partition 116.
  • lubricant commonly lubricating oil
  • the drive shaft 130 is formed with a channel extending substantially along its axial direction, that is, a center hole 136 formed at the lower end of the drive shaft 130 and an eccentric hole 134 extending upward from the center hole 136 to the end surface of the eccentric pin 132.
  • the end of the center hole 136 is immersed in the lubricating oil at the bottom of the compressor housing or is otherwise supplied with lubricating oil.
  • one end of the central hole 136 is supplied with lubricating oil by the lubricating oil supply device.
  • the lubricating oil entering the central hole 136 is pumped or thrown to the eccentric hole 134 by centrifugal force during the rotation of the drive shaft 130 And flow upward along the eccentric hole 134 all the way to the end surface of the eccentric pin 132.
  • the lubricating oil discharged from the end surface of the eccentric pin 132 flows down into the recess 146 of the main bearing housing 140 along the gap between the unloading bush 142 and the eccentric pin 132 and the gap between the unloading bush 142 and the hub 162.
  • the translational rotation of 160 spreads between the end plate of the movable scroll member 160 and the thrust surface of the main bearing housing 140.
  • the lubricating oil supplied to various moving parts in the compressor is thrown out and splashed to form droplets or mist. These lubricating oil droplets or mist will be mixed in the working fluid (mainly refrigerant) sucked from the intake joint 118.
  • the working fluid mixed with the lubricating oil droplets is sucked into the compression chamber between the fixed scroll member 150 and the movable scroll member 160 to achieve lubrication, sealing, and cooling of the scroll members.
  • the working fluid mixed with lubricating oil is compressed by the scroll assembly to become a high-pressure state (gaseous mixture), and enters the external circulation line outside the compressor housing via the exhaust passage 152 and the exhaust joint 119.
  • the inventor realized that it would be advantageous if the sealing effect between the partition plate 116 of the existing compressor and the metal-metal sealing surface of the sealing assembly can be further improved to reduce pressure leakage. Furthermore, it would be more advantageous if the metal-metal sealing surface between the seal ring and the separator 116 can be provided with a lubricating effect to reduce the wear of the sealing surface.
  • the existing baffle-floating seal ring structure scheme has almost no secondary separation of the lubricating oil/refrigerant mixture on the high-pressure side.
  • the lubricating oil mixed in the refrigerant is sucked into the scroll assembly (scroll compression mechanism) and will be directly discharged from the compressor to form a system oil circulation. Therefore, the management of the system oil circulation amount is all concentrated on the low-pressure side of the compressor, that is, the scroll suction side It is difficult to control the oil circulation. Therefore, it is expected to further improve the control of the oil circulation and reduce the difficulty of the oil circulation control.
  • seal-oil interception structure is intended to refer to the diaphragm structure of the scroll compressor And the overall structure formed by the seal assembly matched with it.
  • the improvement of the sealing assembly S relative to the sealing assembly S in FIG. 2b mainly lies in the structure of the upper plate S1. Therefore, for the lower plate and the sealing member, it will not be repeated here.
  • the seal-oil intercepting structure includes: a partition 116, similar to the partition shown in FIG. 1, which defines a central hole 116a through which exhaust gas passes (in this embodiment, the central hole 116a corresponds to the The central channel of the partition unit B also corresponds to the vent hole B1) of the partition unit B, and a wear-resistant gasket 10 is arranged around the central hole 116a at the bottom of the partition 116 to provide a more wear-resistant seal than the partition itself Surface M1 (hereinafter referred to as the first sealing surface M1 for ease of distinction); the sealing assembly S, the top end S11 of the upper plate S1 (see FIG.
  • the sealing assembly S includes a partition for surrounding the central hole S5
  • the first sealing surface M1 of 116 abuts to form a hermetically sealed sealing surface M2 (hereinafter referred to as a second sealing surface M2); a filter device F (corresponding to the oil intercepting device according to the present application), which is installed Above the central hole 116a of the partition 116 and covering the entire central hole 116a (here, it can be understood that the filtering device F can also be installed inside the central hole 116a, and can only cover a part of the central hole 116a, as long as the filtering device F can be A certain amount of oil may be retained) to filter the lubricating oil in the gaseous mixture discharged from the central hole 116a.
  • these gaseous mixtures are roughly composed of a working fluid such as a coolant and lubricating oil.
  • a working fluid such as a coolant and lubricating oil.
  • the oil droplets remaining on the filter device F will drip downward under the action of gravity or flow down the wall of the central hole 116a of the partition 116 into the exhaust passage, and then return to the vortex through the exhaust passage Inside to lubricate and seal the inside of the scroll, improve the compression performance and reliability of the scroll system.
  • the lubricating oil in the exhaust gas is intercepted by the filter device F, the oil content in the exhaust gas of the compressor is significantly reduced, thus reducing the oil circulation rate.
  • the intercepted lubricating oil can be further utilized by slightly modifying the structure of the upper plate S1 of the ordinary sealing assembly S.
  • an improved upper plate S1' is provided.
  • the top end of the upper plate S1' further extends radially inward until it extends beyond the wall surface of the center hole 116a (central passage) of the partition 116.
  • the inner edge portion of the upper plate S1' is formed to be higher than the annular protrusion S12 of the second sealing surface M2 and the annular protrusion S12 and the wall surface of the center hole 116a of the partition 116 in the assembled state will be A gap is left.
  • annular groove can be formed between the annular protrusion S12 and the partition plate 116, and the annular groove will function as an oil storage groove.
  • a groove S10 lower than the second sealing surface M2 may also be provided between the second sealing surface M2 and the annular protrusion S12. It should be noted that the existence of the groove S10 will facilitate the accumulation of intercepted lubricating oil at the top of the upper plate S1', which can better serve as an oil storage tank, but it is not absolutely necessary. In some cases, in order to simplify the structure of the upper plate S1' or save manufacturing costs, the groove S10 may be omitted.
  • a part of the lubricating oil filtered by the filtering device F is allowed to drip into the gap between the annular protrusion S12 and the wall surface of the center hole 116a of the partition 116, and is further received by the groove S10 of the upper plate S1 Receive and store.
  • Depositing a part of the lubricating oil on the oil storage tank will bring various beneficial effects.
  • the accumulated lubricating oil will improve the sealing effect of these poor sealing parts
  • seal-oil interception structure by adding the filter device F at the center hole 116a of the separator and simply improving the upper plate of the seal assembly S, in addition to being able to realize the secondary compression of the lubricant/refrigerant mixture
  • the separation facilitates the management of compressor lubricating oil, and also allows the trapped oil to return to the inside of the scroll or be re-introduced into the low-pressure oil sump side, while providing an additional oil seal to the metal-metal seal MM to reduce pressure leakage, therefore, Greatly improve the stability and compression performance of the compressor operation.
  • the wear-resistant gasket 10 at the bottom of the partition 116 is provided to directly contact the upper plate S1 or the upper plate S1' of the sealing assembly S to form an airtight seal, and thus, since the partition is avoided
  • the direct contact between the 116 and the sealing assembly S reduces the requirements for the material wear resistance of the separator 116, which can save material costs.
  • the wear-resistant gasket 10 can also be omitted, and the partition 116 is directly brought into contact with the upper plate S1 of the sealing assembly S to form a seal.
  • the filtering device in the form of a filter screen can be used as the oil intercepting device according to the present application, other suitable devices capable of trapping and separating oil particles in the exhaust gas, such as guide plates and rotary Cartridges or other feasible oil and gas separators.
  • the sieve material may be any suitable material, for example, it may be any textile fiber sieve or metal sieve having a multilayer structure or a combination of both.
  • additional elements may be provided at the partition 116 to provide improved performance.
  • the additional elements may be installed at the central hole 116a of the partition 116 and form a sealing fit with the central hole 116a and provide resistance ⁇ M1 ⁇ Grinding the first sealing surface M1.
  • the partition Unit B the combination of the partition 116 and the structure installed at the partition 116 to provide the first sealing surface M1 (for example, the wear-resistant gasket 10 described above) will be simply referred to as “the partition Unit B”.
  • add-on devices which may be, for example, separate sealing rings, or other functional components with sealing flanges.
  • the partition unit B includes a partition 116 and a seal ring 20 (corresponding to an additional device) fitted in the central hole 116a of the partition 116,
  • the outer peripheral surface forms an interference fit with the central hole 116a to provide a good airtight seal.
  • the central orifice 23 of the seal ring 20 defines the exhaust hole B1 (again equivalent to the central passage) of the partition unit B, and the lower surface of the seal ring 20 is provided with the upper surface of the upper plate S1 of the seal assembly S.
  • the first sealing surface M1 cooperates with the second sealing surface M2.
  • a dome-shaped filter device F is installed on the sealing ring 20 and covers the central opening 23 of the sealing ring 20 to filter the lubricating oil in the gaseous mixture discharged from the central opening 23.
  • the dome-shaped filter device F is merely an example, which is intended to explain that the shape of the filter device F may be changed according to actual needs, and is not limited to the flat plate shape in the first embodiment. In this configuration, part of the intercepted oil will drop directly through the central orifice 23 of the sealing ring 20 back into the vortex, while a part of the oil will converge to the bottom end of the filter device F and then follow the central orifice The inner wall surface of 23 returns to the inside of the vortex.
  • the annular protrusion S12 of the upper plate S1' is located radially inward of the central opening 23 (ie, the central passage) of the seal ring 20 and leaves a gap with the wall surface of the central opening 23, thereby allowing The lubricating oil filtered by the filtering device F drops into the gap between the annular protrusion S12 and the wall surface of the central orifice 23 and is received and stored by the groove S10, thereby allowing the lubricating oil to flow through the sealing portion MM or overflow to the annular shape Out of the protrusion S12 to achieve the effect as can be provided in the first embodiment.
  • the filter device F in a dome configuration since the filter device F in a dome configuration is adopted, the filtered lubricating oil will be more concentrated toward the bottom and enter the oil storage tank.
  • a conical shape or other advantageous shapes can be used to achieve this purpose.
  • the seal ring 20 can be further improved.
  • the flange of the seal ring 20 is provided with The oil hole 21 communicated with the groove S10 of the upper plate S1' is located at the lower edge of the filter device F, and can just receive the lubricating oil flowing down the filter device F.
  • the oil hole 21 is located on the radially inner side of the metal-metal seal portion M-M.
  • the upper surface of the flange of the sealing ring 20 may also be provided with an oil guide groove 22 which facilitates receiving the lubricating oil dripping from the filtering device F and guiding the lubricating oil into the oil hole 21 to reach the upper plate S1
  • the annular groove between the annular protrusion S12 of the upper plate S1' and the wall surface of the central opening 23 will To the oil storage tank, at the same time, a part of oil can also be stored in the oil hole 21, the oil in the oil hole 21 can also play the role of providing an additional oil seal to the metal sealing portion MM, and when the first sealing surface M1 and the second When a radial gap occurs between the sealing surfaces M2, the oil holes 21 will communicate with the annular groove. At least a part of the oil received by the two will flow and mix on the second sealing surface M2, and a part will flow into the low pressure side. A part will remain in the oil hole 21 or the annular groove.
  • the bottom end of the filter device F, the oil guide groove 22, the oil hole 21, and the groove S10 are aligned in the vertical direction as much as possible to efficiently receive and guide the filtered lubricating oil to the storage Oil tank.
  • one or more oil holes 21 may be provided, the position and number of the oil guide grooves 22 may correspond to the position and number of the oil holes 21, or the oil guide groove 22 may also be a single through each oil hole 21 Circular groove.
  • Figures 5a to 5e show another possible form of the seal-oil intercepting structure according to the present application.
  • the partition unit B is provided with a cylindrical body formed integrally or separately with a seal ring (for example, the seal ring 20).
  • the additional device is no longer a separate sealing ring 20, but a sound-absorbing assembly (wear-resistant element) 30 composed of a sealing flange (equivalent to a sealing ring) and a cylinder, the sound-absorbing assembly 30 Of the flange fits tightly in the central hole 116a and provides the first sealing surface M1 and the central opening 34.
  • the central opening 34 and the internal passage of the barrel together constitute the central passage of the partition unit B, as shown in FIG.
  • FIG. 5a A schematic diagram of the sound attenuation assembly 30 is shown.
  • the provision of a noise reduction assembly at the central hole 116a helps to reduce the exhaust noise of the compressor.
  • the top of the muffler assembly 30 is closed, and only has a plurality of exhaust holes 33 distributed on the side surface that serve as the exhaust holes B1 of the partition unit B, so it is an optional Installation method, as shown in FIG. 5b, the filter device F may be installed at the central opening 34 of the muffler assembly 30 to completely or partially cover the central opening 34 to intercept the exhaust gas to be passed through the plurality of exhaust holes 33 Lubricating oil.
  • the filter device F is set to a configuration with a high center and a low circumference, such as a dome shape or a conical shape, so that the filtered oil flows around the filter device F and is more collect.
  • FIGS. 5c to 5e show another optional installation method of the filter device F.
  • the filter device F no longer completely surrounds the entire noise reduction assembly, but is adapted to be installed in a cylindrical shape
  • 5d shows an assembly state diagram.
  • an oil hole 31 provided on the flange of the muffler assembly 30 needs to be provided for providing a path for the lubricating oil in the filter device F to return to the inside of the scroll .
  • FIG. 5e shows the oil hole 31 arranged corresponding to the oil hole 31.
  • the oil guide groove 32 is not necessary, and the arrangement of the oil hole 31 and the oil guide groove 32 can have various alternatives. The form is not limited to what is shown here.
  • oil holes 21 and 31 are shown in the form of cylindrical through holes in the drawings of the present application, those skilled in the art can easily conceive various modifications, for example Collect and guide the lubricating oil well, the oil hole can also be in the shape of an inverted cone, or it can be an inverted conical flared part at the upper part, a cylindrical configuration at the lower part, etc. Will be advantageous.
  • the flange of the silencer assembly 30 serves as a so-called wear-resistant element that provides the first sealing surface M1.
  • the configuration of the filter device can be designed in an advantageous manner according to the configuration of the separator unit, as long as the filter device can achieve effective filtration of the mixed gas discharged from the separator unit Yes, but not limited to the configuration given in the examples herein.
  • the filter device F may have a split structure.
  • FIG. 6a shows a fourth embodiment of the seal-oil interception structure, in which the additional device is replaced by a silencer assembly 30 with a cylindrical assembly 40 with at least one side hole 43.
  • the cylindrical portion of the cylindrical assembly 40 may also be other members with side holes, for example, it may be a bracket surrounded by a frame for supporting the filter, or any other function with other additional functions Devices (including but not limited to the aforementioned silencer).
  • the filtering device F is no longer completely enclosed outside the central hole 116a, but is directly installed in the corresponding side hole 43 in the form of a plurality of independent individuals.
  • the advantages of this split-type filter device F are obvious. For example, it can save filter materials and reduce production costs. When a filter element needs to be repaired or replaced, only the filter element can be maintained or replaced, thereby reducing Update and maintenance costs.
  • part of the oil trapped via the filter device F can flow down the inner wall of the cylindrical portion back to the inside of the vortex.
  • at least one oil hole 41 may be provided at the bottom flange of the cylindrical assembly 40.
  • the number and position of 41 preferably correspond to the number and position of side holes 43.
  • the oil hole 21 is located radially inward of the metal-metal seal portion M-M. This may allow a part of the oil trapped via the filter device F to flow down the outer wall of the cylindrical portion back to the inside of the vortex.
  • the upper plate S1 of the seal assembly S is replaced with the upper plate S1' as shown in FIG. 3b, in this case, it is allowed to guide a part of the oil trapped via the filter device F to the low-pressure side.
  • at least one vertical guide groove 44 communicating with the oil hole 41 may be provided below the side hole 43 where the filter device F is installed, The improved form is shown in Figure 6b.
  • the oil guide groove is not an absolutely necessary structure and can be omitted in appropriate cases, or can be The oil is guided to the oil hole instead of other structures.

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Abstract

一种具有密封‑截油结构的涡旋压缩机，包括：隔板单元（116），其具有供排出气体通过的孔口以及位于隔板单元（116）的底侧且围绕孔口的第一密封面（M1）；布置在隔板单元下方的密封组件（S），并且在其顶端包括构造成围绕密封组件（S）的中心孔的第二密封面（M2），第二密封面（M2）抵靠第一密封面（M1）从而形成分隔高压侧与低压侧的密封；以及设置在隔板单元的孔口处以截留排出气体中油的截油装置（F），其允许所截留的油回流经过隔板单元。压缩机能够将一部分润滑油重新导入涡旋内部以及/或者重新导入低压油池侧，从而提高压缩机的压缩性能和运行稳定性，并且降低油循环率。

Description

具有密封-截油结构的涡旋压缩机
本申请要求于2018年11月29日提交中国专利局、申请号为201811443483.7、名称为“具有密封-截油结构的涡旋压缩机”的中国专利申请以及于2018年11月29日提交中国专利局、申请号为201821990326.3、名称为“具有密封-截油结构的涡旋压缩机”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
本申请涉及一种具有密封-截油结构的涡旋压缩机。。
背景技术
本部分的内容仅提供了与本公开相关的背景信息，其可能并不构成现有技术。
涡旋压缩机通常包括由定涡旋部件和动涡旋部件构成的压缩机构。该压缩机构用于将来自低压侧的工作流体压缩成高压状态并经高压侧的排气接头排出到外部循环管路中。通常，压缩机中的润滑剂由于压缩机中各种活动部件的运动而形成液滴或雾并且混合在工作流体中。混合在工作流体中的这些润滑剂液滴或雾从低压侧的吸气口吸入到由定涡旋部件和动涡旋部件限定的一系列压缩腔中以起到润滑、密封、冷却等作用。最后混合有润滑剂的工作流体通过涡旋组件压缩变成高压状态(气态混合物)后经由高压侧的排气接头进入到压缩机壳体之外的外部循环管路中。
为了确保压缩机的压缩性能，在压缩机内部设置有将压缩机的内部空间分隔成高压侧和低压侧的隔板以及相应的密封组件。密封组件设置在定涡旋部件的端板上的凹部中。密封组件(尤其是浮动密封组件)包括上板、下板以及设置在上板与下板之间的密封件，上板的顶端可以抵靠隔板上的套环或者直接抵靠隔板的下表面进行密封以实现高压侧与低压侧的有效分隔。然而，在本领域中，依然存在减小系统油循环、改善对涡旋结构的润滑、改善密封组件与隔板(或隔板套环)之间的密封性能和磨损状况的空间和需求。
发明内容
本申请的一个目的是提供一种能够对涡旋内部进行额外的润滑和密封的涡旋压缩机。
本申请的另一目的是提供一种用于涡旋压缩机的能够改善密封圈和隔板之间的金属-金属密封的密封性能的密封-截油结构。
本申请的再一目的是提供一种用于涡旋压缩机的能够减少密封圈和隔板之间的金属-金属密封面的磨损的密封-截油结构。
本申请的又一目的是提供一种能够有利于压缩机润滑油的管理的涡旋压缩机。
根据本申请的一个方面，提供了一种涡旋压缩机，包括：隔板单元，隔板单元具有供排出气体通过的排气孔以及位于隔板单元的底侧的第一密封面；以及密封组件，密封组件布置在隔板单元下方、并且在顶端包括构造成围绕密封组件的中心孔的第二密封面，第二密封面抵靠第一密封面从而形成分隔高压侧与低压侧的密封部，涡旋压缩机还包括截油装置，截油装置设置在隔板单元的排气孔处以截留排出气体中的油并允许所截留的油回流经过隔板单元。
可选地，隔板单元包括限定出排气孔的隔板以及围绕排气孔设置在隔板的底侧的耐磨垫片，耐磨垫片的底表面提供第一密封面。
可选地，隔板单元包括具有中心孔的隔板以及安装在隔板的中心孔内的附加装置，附加装置限定出隔板单元的排气孔以及第一密封面。
可选地，附加装置为密封环，密封环的中央孔口限定隔板单元的排气孔，并且密封环的底面提供第一密封面。
进一步，附加装置可以包括密封环以及与密封环一体或分体形成的筒体，筒体围绕密封环的中央孔口向上延伸，并且筒体上设置有用作隔板单元的排气孔的至少一个孔口，密封环的底面提供第一密封面。
可选地，截油装置以横跨筒体的内径的方式设置在筒体内以拦截待经过筒体上的所述至少一个孔口排出的所述排出气体中的油。
替代性地，截油装置在密封环上方一体地包围在筒体外侧。
可选地，至少一个孔口设置在筒体的侧壁上。截油装置可以呈分体形式分别设置在筒体上的所述至少一个孔口中。
优选地，密封组件的顶端径向向内延伸超过隔板单元的中央通道的壁面，并且顶端的内边缘设置有在隔板单元的中央通道的壁面的径向内侧向上突出的突出部，其中，突出部与中央通道的壁面之间留有间隙以便接收从截油装置 滴落的油的至少一部分。
根据需要，可以在密封环中设置至少一个油孔，油孔的数量和位置设定成适于接收来自所述截油装置的油，并且油孔定位成在组装状态下位于密封部的径向内侧。
油孔可以是圆柱形通孔、倒锥形通孔或上端带有扩口部的通孔。
可以在密封环上设置导油槽，导油槽位于油孔上方以用于接收从截油装置滴落的油并且将油引导到油孔中。
优选地，密封组件的顶端上还可以设置有位于第二密封面与突出部之间的凹槽，凹槽在组装状态下位于油孔下方，以接收来自油孔和间隙的油。
筒体可以构造为适于减小排气噪音的消音罩。
截油装置可以为带有滤网的过滤装置。过滤装置可以是一体式过滤装置，其能够根据所述隔板单元的排气孔的布置适配成呈平板状、穹顶状、圆锥状或有顶筒状；当隔板单元具有多个排气孔时，过滤装置也可以是分别设置在隔板单元的排气孔处的分体式过滤装置。
截油装置可以是多层纺织纤维滤网或多层金属丝滤网。
密封组件可以是设置在涡旋压缩机的定涡旋端板处的凹部中的浮动密封圈组件，并且顶端由浮动密封圈组件的上板提供。
第一密封面与第二密封面之间为金属-金属密封。
作为一个有利效果，根据本申请的压缩机能够实现对润滑油/制冷剂混合物压缩后的二次分离，并利用泄漏通道将润滑油重新导入涡旋内部对涡旋内部进行润滑和密封，提高涡旋的工作性能和可靠性。
作为另一有利效果，根据本申请的压缩机还能够允许一部分截留出的油利用金属-金属密封面之间因变形或相对运动等原因而产生的泄漏通道重新导入低压油池侧，这能够进一步提高压缩机运行的稳定性和压缩性能：一方面，将分离出的润滑油引导至密封圈和隔板之间的金属-金属密封面处进行油密封，从而提高密封性能；另一方面，能够引导润滑油对密封圈和隔板之间的金属-金属密封面进行润滑，从而减少因相对运动导致的磨损。
作为又一有利效果，由于使压缩机排出气体中的含油比例降低，由此降低了油循环率，降低油循环率有利于压缩机润滑油的管理，有利于提高系统的 应用可靠性及性能。
附图说明
通过以下参照附图的描述，本申请的一个或几个实施方式的特征和优点将变得更加容易理解。这里所描述的附图仅是出于说明目的而并非意图以任何方式限制本申请的范围，附图并非按比例绘制，可放大或缩小一些特征以显示特定部件的细节。在附图中：
图1是常规的涡旋压缩机的纵剖视图；
图2a是示意性地示出了图1中所示的涡旋压缩机内压力分布的纵剖视图；
图2b是一种双板浮动密封圈组件的分解视图；
图2c示意性地示出了隔板与密封组件之间的金属-金属密封部；
图3a是根据本申请的第一实施方式的涡旋压缩机的局部剖视图；
图3b是带有突出部的密封组件的上板的剖视立体图；
图3c是图3a所示涡旋压缩机的改进形式的局部剖视图，其中包括图3b所示的密封组件的上板，并且以箭头标示了排出气体中的润滑油的行进路线；
图4a是根据本申请的第二实施方式的涡旋压缩机的局部剖视图；
图4b是图4a所示涡旋压缩机的改进形式的局部剖视图，其中包括图3b所示的密封组件的上板；
图5a是应用于本申请的第三实施方式中的消音组件的立体图；
图5b是根据本申请的第三实施方式的涡旋压缩机的局部剖视图；
图5c是示出了根据本申请的第三实施方式的隔板单元与过滤装置的另一组合形式的立体剖视图；
图5d是包括图5c中的隔板单元与过滤装置的涡旋压缩机的局部剖视图；
图5e是图5d所示的涡旋压缩机的改进形式的局部剖视图，其中包括图3b所示的密封组件的上板，并且以箭头标示了排出气体中的润滑油的行进路线；
图6a是包括根据本申请的第四实施方式的密封-截油结构的涡旋压缩机的局部剖视图；以及
图6b是图6a所示的涡旋压缩机的改进形式的局部剖视图，其中包括图 3b所示的密封组件的上板。
具体实施方式
下面对本申请各种实施方式的描述仅仅是示例性的，而绝不是对本申请及其应用或用法的限制。在各个附图中采用相同的附图标记来表示相同的部件，因此相同部件的构造将不再重复描述。
首先将参照图1描述涡旋压缩机的总体构造和运行原理。如图1所示，涡旋压缩机100(下文中有时也会称为压缩机)一般包括壳体110。壳体110可以包括大致圆筒形的本体111，设置在本体111上端的顶盖112、位于本体111下方的底盖114以及设置在顶盖112与本体111之间以将压缩机的内部空间分隔成高压侧和低压侧的隔板116。如在图2a示意性地示出的，隔板116与顶盖112之间的空间构成高压侧HC，而隔板116下方的涡旋组件外围的空间则构成低压侧LC。在低压侧LC设置有用于吸入流体的进气接头118，在高压侧HC设置有用于排出压缩后的流体的排气接头119。壳体中设置有由定子122和转子124构成的马达120。转子124中设置有驱动轴130以驱动由定涡旋部件150和动涡旋部件160构成的压缩机构。定涡旋部件150包括设置在端板上方的用于形成凹部158的分体环形构件154。在环形构件154在内侧限定有排气通道152。排气通道152的空间也构成高压侧HC。
为了实现流体的压缩，定涡旋部件150与动涡旋部件160之间需要有效密封，并且各活动部件之间也需要有良好的润滑。
作为压缩机密封的一个重要方面，通常，在定涡旋部件150的凹部158中设置有密封组件(例如浮动密封圈组件)S。即，密封组件S设置在隔板116与定涡旋部件150之间。密封组件S与凹部158一起配合形成为定涡旋部件150提供背压的背压腔BC，背压腔内的压力低于高压侧但高于低压侧，即相当于中间压力区MC。
如图2b所示，密封组件S可以包括上板S1、下板S2和设置在上板S1与下板S2之间的第一密封件S3和第二密封件S4。密封组件S的形状与凹部158的形状基本对应，从而第一密封件S3可以抵靠凹部158的径向内侧壁实现密封，而第二密封件S4可以抵靠凹部158的径向外侧壁实现密封。此外，上板S1的顶端S11可以抵靠安装在隔板116上的耐磨元件(例如如下文所述 的耐磨垫片或密封环的底侧)或直接抵靠隔板116的密封部以实现密封进而实现高压侧和低压侧的隔开，图2c示出了上板S1的顶端S11与隔板116之间的金属-金属密封部M-M。在压缩机工作过程中，上板S1与隔板116或隔板116的耐磨元件之间的金属-金属密封部M-M的两个密封面之间会存在微量的相对运动，以适应涡旋组件在运行过程中的微量晃动。
为确保压缩机中各个部件之间的相对运动平稳地进行，需要对压缩机的内部活动元件特别是压缩组件提供良好的润滑。在图1所示的立式涡旋压缩机的示例中，在压缩机壳体的底部存储有润滑剂(常见为润滑油)。相应地，在驱动轴130中形成有大致沿其轴向延伸的通道，即形成在驱动轴130下端的中心孔136和从中心孔136向上延伸到偏心销132端面的偏心孔134。中心孔136的端部浸没在压缩机壳体底部的润滑油中或者以其他方式被供给润滑油。在压缩机的运转过程中，中心孔136的一端被润滑油供给装置供给润滑油，进入中心孔136的润滑油在驱动轴130旋转过程中受到离心力的作用而被泵送或甩到偏心孔134中并且沿着偏心孔134向上流动一直到达偏心销132的端面。从偏心销132的端面排出的润滑油沿着卸载衬套142与偏心销132之间的间隙以及卸载衬套142与毂部162之间的间隙向下流动到达主轴承座140的凹部146中。聚集在凹部146中的一部分润滑油流动穿过主轴承144向下流动，一部分润滑油被毂部162搅动而向上运动到达动涡旋部件160的端板164的下侧并随着动涡旋部件160的平动转动而遍布动涡旋部件160的端板与主轴承座140的止推表面之间。在压缩机的运转过程中，供给到压缩机中的各种活动部件上的润滑油被甩出和飞溅以形成液滴或雾。这些润滑油液滴或雾将混合在从进气接头118吸入的工作流体(主要是制冷剂)中。随后这些混合有润滑油液滴的工作流体被吸入到定涡旋部件150和动涡旋部件160之间的压缩腔中以实现这些涡旋部件的润滑、密封和冷却。最后混合有润滑油的工作流体通过涡旋组件压缩变成高压状态(气态混合物)，经由排气通道152和排气接头119进入到压缩机壳体之外的外部循环管路中。
如前所述，由于压缩机的隔板116与密封组件S的金属-金属密封部M-M之间存在微量晃动，这不可避免地会导致密封面的变形以及磨损问题。该金属-金属密封面若发生变形则会存在泄漏间隙，变形越严重则泄漏量越大，进而 导致压缩机性能下降，特别是变频压缩机低速运行时性能下降。而密封组件S与隔板116之间的金属-金属密封面的磨损同样会导致密封性能的下降。
因此，发明人意识到，如果能够进一步改善现有压缩机的隔板116与密封组件的金属-金属密封面之间密封效果以减少压力泄漏将会是有利的。更进一步，如果能够为密封圈与隔板116之间的金属-金属密封面提供润滑效果从而减少密封面的磨损将是更为有利的。
另外，现有的隔板-浮动密封圈结构方案几乎没有润滑油/制冷剂混合物在高压侧的二次分离。混合在制冷剂中的润滑油被吸入涡旋组件(涡旋压缩机构)后会直接排出压缩机，形成系统油循环，因此系统油循环量的管理全部集中在压缩机低压侧即涡旋吸入侧，油循环控制的难度较大，因此，期望能够进一步改善对油循环的控制，降低对油循环的控制难度。
发明人基于上述原理和思考，提出了一种改进的密封-截油结构以解决上述问题中的至少一个，在此，“密封-截油结构”意在指代涡旋压缩机的隔板结构以及与之配合的密封组件所构成的整体结构。
现在将参照图3a至图6b描述本申请所涉及的密封-截油结构。
在本申请中，密封组件S相对于图2b中的密封组件S的改进之处主要在于上板S1的结构，因此，对于下板和密封件，本文将不再赘述。
下面参照图3a详细描述根据本申请第一实施方式的密封-截油结构。该密封-截油结构包括：隔板116，类似于图1中所示的隔板，其限定出供排出气体通过的中心孔116a(在该实施方式中，中心孔116a对应于根据本申请的隔板单元B的中央通道，也对应于隔板单元B的排气孔B1)，在隔板116的底部围绕中心孔116a布置有耐磨垫片10以提供比隔板本身更加耐磨的密封面M1(为便于区分，在下文中称为第一密封面M1)；密封组件S，该密封组件S的上板S1(例如参见图2b)的顶端S11包括围绕中心孔S5的用于与隔板116的第一密封面M1相抵靠从而构成气密密封的密封面M2(在下文中称为第二密封面M2)；过滤装置F(对应于根据本申请的截油装置)，该过滤装置F安装在隔板116的中心孔116a上方并且覆盖整个中心孔116a(这里，可以理解，过滤装置F也可以安装在中心孔116a内部，并且可以只覆盖中心孔116a的一部分，只要使得该过滤装置F能够截留一定的油即可)，以过滤从中心孔 116a排出的气态混合物中的润滑油。如前文所述的，这些气态混合物大致由冷却剂等工作流体和润滑油组成，经过过滤装置F的过滤，混合气体中的至少一部分润滑油被过滤下来并存留在过滤装置F上。存留在过滤装置F上的油滴会在重力作用下会向下滴落或是顺着隔板116的中心孔116a的壁面向下流动进入排气通道，进而穿过排气通道回流至涡旋内部以对涡旋内部进行润滑和密封，提高涡旋系统的压缩性能和可靠性。另外，由于通过过滤装置F拦截了排出气体中的润滑油，使得压缩机排出气体中的含油比例明显降低，因此降低了油循环率。这对于压缩机润滑油的管理以及提高系统的应用可靠性及性能是非常有利的：第一，压缩机排出气体中含油比例小有利于提高整个制冷/制热循环的能效(换热器效率更高)；第二，压缩机排出气体中含油比例小有利于维持压缩机内部油量，提高压缩机运行的可靠性。
作为一个改进方案，发明人设想到可以通过将普通的密封组件S的上板S1进行结构上的略微改动来进一步利用被拦截的润滑油。如图3b中所示，提供了一种改进的上板S1’。相对于上板S1而言，上板S1’的顶端进一步径向向内延伸，直到延伸超出隔板116的中心孔116a(中央通道)的壁面。其中，在上板S1’的内边缘部形成为高于该第二密封面M2的环形突出部S12并且使得在组装状态下该环形突出部S12与隔板116的中心孔116a的壁面之间将留有间隙，通过设置这一间隙，可以使得环形突出部S12与隔板116之间形成环形槽，该环形槽将起到储油槽的作用。优选地，如图3b所示，还可以在第二密封面M2与环形突出部S12之间设置低于第二密封面M2的凹槽S10。应注意的是，该凹槽S10的存在将有利于被拦截的润滑油在上板S1’的顶端的积累，其可以更好地起到储油槽的作用，然而其并非是绝对必要的，在某些情况下，为了简化上板S1’的结构或节约制造成本，可以省略该凹槽S10。
如图3c示出了将第一实施例中的上板S1替换成上板S1’之后的构造，其中，上板S1的环形突出部S12位于隔板116的中心孔116a(相当于中央通道)的内侧并且环形突出部S12的外壁与中心孔116a的内壁之间留有间隙。通过这样的设置，允许被过滤装置F过滤下的润滑油有一部分滴落到环形突出部S12与隔板116的中心孔116a的壁面之间的间隙中，并进而被上板S1的凹槽S10接收并储存。可以设想到，在没有设置凹槽S10的情况下，滴落的一部分 润滑油将储存在环形突出部S12与隔板116的中心孔116a的壁面之间的环形槽中，此时，环形突出部S12与隔板116的中心孔116a的壁面之间的空间将起到储油槽的作用。
使一部分润滑油沉积在储油槽上将带来多种有利效果，首先，其能够为金属-金属密封部M-M提供额外的油密封效果，特别是在该金属-金属密封部M-M处存在例如由于变形等原因产生的密封不良部位的情况下，积聚的润滑油将改善这些密封不良部位的密封效果；其次，当涡旋组件在运行过程中发生微量晃动时，金属-金属密封部M-M会因相对运动(特别是纵向方向上)而出现微小间隙，积存在储油槽中的部分润滑油在高压侧与低压侧之间的压差作用下经由该微小间隙而被挤压出金属-金属密封部M-M，进而流回到低压侧并且回流至压缩机底部油池；第三，如果储油槽中的油量超出该储油槽的容量时，过量的油可以溢出到环形突出部S12之外从而回流至涡旋内部。在图3c中，为便于理解，以箭头示出了混合物中润滑油的流动路线。
换言之，采用上述密封-截油结构，通过在隔板中心孔116a处增加过滤装置F以及对密封组件S的上板进行简单的改进，除了能够实现对润滑油/制冷剂混合物压缩后的二次分离从而便于压缩机润滑油的管理，还能够允许截留出的油回流至涡旋内部或重新导入低压油池侧，同时对金属-金属密封部M-M提供额外的油密封进而减少压力泄漏，因此，大大提高了压缩机运行的稳定性和压缩性能。
此外，在前述实施方式中，提供了位于隔板116底部的耐磨垫片10来与密封组件S的上板S1或上板S1’直接接触以形成气密密封，这样，由于避免了隔板116与密封组件S的直接接触，因此降低了隔板116对材料耐磨性的要求，可以节省材料成本。然而，对于本领域技术人员而言明显的是，也可以省略该耐磨垫片10，而使隔板116与密封组件S的上板S1直接接触以形成密封。
这里，需要指出的是，除了滤网形式的过滤装置可以用作根据本申请的截油装置之外，也可以使用能够截留和分离排出气体中的油颗粒的其他合适的装置，例如导板和旋筒或者其他可行的油气分离器等。在包括滤网的情况下，滤网材料可以是任何适用的材料，例如可以是具有多层结构的任何纺织纤维滤网或五金滤网或两者的组合。
在一些实际应用中，隔板116处可能还设置有额外的元件以提供改进的性能，所述额外的元件可以安装在隔板116的中心孔116a处且与中心孔116a形成密封配合并且提供耐磨的第一密封面M1。为了便于描述，在下文中，隔板116以及安装在隔板116处的用于提供第一密封面M1的结构(例如，上文所述的耐磨垫片10)的组合将简称为“隔板单元B”。并且上述额外的元件将统称为“附加装置”，其例如可以是单独的密封圈，也可是带有密封凸缘的其他功能性组件。
作为示例，在图4a所示的第二实施方式中，隔板单元B包括隔板116和配合在隔板116的中心孔116a中的密封环20(对应于附加装置)，该密封环20的外周面与中心孔116a形成过盈配合以提供良好的气密密封。在此情况下，密封环20的中央孔口23限定出隔板单元B的排气孔B1(又相当于中央通道)，并且密封环20的下表面提供与密封组件S的上板S1的第二密封面M2相配合的第一密封面M1。穹顶状的过滤装置F安装在密封环20上并且覆盖密封环20的中央孔口23，以过滤从中央孔口23中排出的气态混合物中的润滑油。在此，穹顶状的过滤装置F仅作为示例，其意在说明过滤装置F的形状可以根据实际需求而变化，而不限于第一实施方式中的平板状。在该构造中，拦截到的油液将有一部分直接经过密封环20的中央孔口23滴落回涡旋内部，而有一部分油液将汇聚至过滤装置F的底端然后顺着中央孔口23的内壁面回流至涡旋内部。
在该实施方式中，将密封组件S的上板S1替换为如图3b中所示的上板S1’将是特别有利的。如图4b所示，上板S1’的环形突出部S12位于密封环20的中央孔口23(即中央通道)的径向内侧并且与中央孔口23的壁面之间留有间隙，由此允许被过滤装置F过滤出的润滑油滴落到环形突出部S12与中央孔口23的壁面之间的间隙中并且被凹槽S10接收并储存，从而允许润滑油流动经过密封部M-M或溢出到环形突出部S12之外以实现如在第一实施方式中所能提供的效果。在此，由于采用了呈穹顶构型的过滤装置F，将使得过滤出的润滑油更大程度地向底部汇聚从而进入储油槽中。本领域技术人员可以容易地设想到，除了穹顶型，还可以采用比如圆锥形或其他有利的形状来实现这一目的。
在此基础上，为了更好地促进过滤装置F中的润滑油进入储油槽，还可以对密封环20作进一步的改进，例如如图4b所示，在密封环20的凸缘中设置有与上板S1’的凹槽S10连通的油孔21，该油孔21位于过滤装置F的下边缘处，刚好可以接收沿着过滤装置F流下的润滑油。在安装状态下，油孔21位于金属-金属密封部M-M的径向内侧。更有利地，在密封环20的凸缘的上表面还可以设置有导油槽22，该导油槽便于接收从过滤装置F滴落的润滑油并且将引导润滑油进入油孔21进而到达上板S1的储油槽S10中。然而，可以设想到，在上板S1’的顶端未设置凹槽S10的情况下，上板S1’的环形突出部S12与中央孔口23(即中央通道)的壁面之间的环形槽将起到储油槽的作用，同时油孔21中也可以储存一部分油，油孔21中的油同样可以起到对金属密封部M-M提供额外的油密封的作用，而当第一密封面M1与第二密封面M2之间产生径向间隙时，油孔21将与环形槽相连通，两者所接收到油的至少一部分将在第二密封面M2上流动并混合，一部分将流入到低压侧，还有一部分将残留在油孔21或环形槽中。
优选地，在组装状态下，过滤装置F的底端、导油槽22、油孔21以及凹槽S10在竖向方向上尽可能地对准，以高效地接收和引导过滤出的润滑油到达储油槽。可选地，油孔21可以设置有一个或多个，导油槽22的位置和数量可以与油孔21的位置和数量相对应，或者导油槽22也可以是贯通各个油孔21的一个单独的圆环形凹槽。
图5a至5e示出了根据本申请的密封-截油结构的另一种可能的形式。在该第三实施方式中，隔板单元B设置有与密封环(例如密封环20)一体或分体地形成的筒体。或者说，在该实施方式中，附加装置不再是单独的密封环20，而是由密封凸缘(相当于密封环)和筒体组成的消音组件(耐磨元件)30，该消音组件30的凸缘紧密配合在中心孔116a中并且提供第一密封面M1以及中心孔口34，此时，中心孔口34与筒体的内部通道共同构成隔板单元B的中央通道，图5a示出了消音组件30的示意图。在实际应用中，在中心孔116a处设置消音组件有助于减小压缩机的排气噪音。如图中所示，消音组件30的顶部是封闭的，而仅具有分布在侧表面上的用作隔板单元B的排气孔B1的多个排气孔33，因此作为一种可选的安装方式，如图5b所示，可以将过滤装置 F安装在消音组件30的中心孔口34处，以完全地或部分地覆盖中心孔口34从而拦截待经过多个排气孔33的排出气体中的润滑油。
另外，可以设想，在此基础上，还可以将密封组件S的上板S1替换为如图3b中所示的上板S1’。在组装状态下(未图示)，上板S1’的环形突出部S12位于消音组件30的中心孔口34的径向内侧并且与中心孔口34的壁面之间留有间隙，由此允许被过滤装置F过滤出的润滑油滴落并存储在环形突出部S12与中央孔口23的壁面之间，以产生如在第一实施方式中所能实现的技术效果。同样地，在此情形下，可以设想将过滤装置F设置成中间高四周低的构型如穹顶型或圆锥形等以便于使过滤出的油在过滤装置F中向四周流动进而更多地被收集。
图5c至图5e示出了过滤装置F的另一种可选的安装方式，如图5c所示，过滤装置F不再是完全地包围整个消音组件，而是适配成呈圆筒状安装在消音组件30的凸缘上并且仅包围侧壁上的排气孔33。图5d示出了组装状态图，在该实施方式中，需要提供设置在消音组件30的凸缘上的油孔31，以用于提供使过滤装置F中的润滑油回流至涡旋内部的路径。
如图5e所示，若将密封组件S的上板S1替换为如图3b中所示的上板S1’，在组装状态下，油孔31位于金属-金属密封部M-M的径向内侧。该油孔31将提供汇入到储油槽中的路径，图5e中还分别以空心箭头和实心箭头示出了混合物中气体和润滑油的流动路径。另外，图5e中还示出了对应于油孔31布置的导油槽32，如前文所述的，导油槽32不是必要的，并且油孔31和导油槽32的布置可以有各种不同的替代形式而不限于在此所示出的。
此外，尽管在本申请的附图中，油孔21和31是以圆柱形通孔的形式示出的，然而本领域技术人员也可以容易地设想到各种不同形式的改型，例如为了更好地收集和引导润滑油，油孔还可以呈倒锥形，或者也可以是上部为倒锥形扩口部、下部呈圆柱形的构型等，这样的油孔构型在不设置导油槽的情况下将是有利的。
在该实施方式中，消音组件30的凸缘充当提供第一密封面M1的所谓耐磨元件。
特别地，对本领域技术人员而言明显的是，过滤装置的构型可以根据隔 板单元的构造而以有利的方式设计，只要过滤装置能够实现对从隔板单元排出的混合气体的有效过滤即可，而决不仅限于本文实施例中所给出的构型。
另外，过滤装置F也可以具有分体式构造。作为示例，图6a示出了密封-截油结构的第四实施方式，在该实施方式中，附加装置由消音组件30替换为带有至少一个侧孔43的筒形组件40。然而，筒形组件40中的筒形部也可以是带有侧孔的其他构件，例如，其可以是由边框围成的用于支撑滤网的支架，也可以是带有其他附加功能的任何装置(包括但不限于前述消音罩)。在该实施方式中，过滤装置F不再是整个地包围在中心孔116a外侧，而是以多个独立个体的形式直接安装在对应的侧孔43中。这种分体式构造的过滤装置F所具有的优点是明显的，例如可以节约过滤材料、降低生产成本，当一处的过滤元件需要维修或更换时，可以仅维护或更换该过滤元件，从而降低更新和维护成本。
在该实施方式，经由过滤装置F截留出的一部分油能够顺着筒形部的内壁向下流动返回至涡旋内部。另外，还可以设想到的是，为了便于将过滤装置F中的润滑油更大程度地引导返回至涡旋内部，可以在筒形组件40的底部凸缘处设置至少一个油孔41，油孔41的数量和位置优选地对应于侧孔43的数量和位置。在组装状态下，油孔21位于金属-金属密封部M-M的径向内侧。这样可以允许经由过滤装置F截留出的一部分油还能够顺着筒形部的外壁向下流动返回至涡旋内部。
如果将密封组件S的上板S1替换为如图3b中所示的上板S1’，在此情况下，则允许将经由过滤装置F截留出的一部分油引导至低压侧。为了更好地将滤装置F中的润滑油引导至油孔41和储油槽中，可以在安装有过滤装置F的侧孔43的下方设置连通至油孔41的至少一个竖向引导槽44，所述改进形式如图6b中所示。
本领域技术人员还可以理解的是，尽管在该示例性实施方式中同时设置了油孔和导油槽，但导油槽并非是绝对必要的结构，在适当情况下可以省略，或者可以由适于将油向油孔引导的其他结构代替。
上文已经具体描述了本申请的各种实施方式和变型，但是本领域技术人员应该理解，本申请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，在不偏离本申请的实质和范围的情况下可由本领域的技术人员实现其它的变型和变体。所有这些变型和变体都落入本申请的范围内。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 (22)

  1. 一种涡旋压缩机，包括：
    隔板单元，所述隔板单元具有供排出气体通过的排气孔以及位于所述隔板单元的底侧的第一密封面；以及
    密封组件，所述密封组件布置在所述隔板单元下方、并且在顶端包括构造成围绕所述密封组件的中心孔的第二密封面，所述第二密封面抵靠所述第一密封面从而形成分隔高压侧与低压侧的密封部，
    其特征在于，
    所述涡旋压缩机还包括截油装置，所述截油装置设置在所述隔板单元的排气孔处以截留所述排出气体中的油并允许所截留的油回流经过所述隔板单元。
  2. 根据权利要求1所述的涡旋压缩机，其中，所述隔板单元包括限定出所述排气孔的隔板以及围绕所述排气孔设置在所述隔板的底侧的耐磨垫片，所述耐磨垫片的底表面提供所述第一密封面。
  3. 根据权利要求1所述的涡旋压缩机，其中，所述隔板单元包括具有中心孔的隔板以及安装在所述隔板的中心孔内的附加装置，所述附加装置限定出所述隔板单元的排气孔以及所述第一密封面。
  4. 根据权利要求3所述的涡旋压缩机，其中，所述附加装置为密封环，所述密封环的中央孔口限定所述隔板单元的排气孔，并且所述密封环的底面提供所述第一密封面。
  5. 根据权利要求3所述的涡旋压缩机，其中，所述附加装置包括密封环以及与所述密封环一体或分体形成的筒体，所述筒体围绕所述密封环的中央孔口向上延伸，并且所述筒体上设置有用作所述隔板单元的排气孔的至少一个孔口，所述密封环的底面提供所述第一密封面。
  6. 根据权利要求5所述的涡旋压缩机，其中，所述截油装置以横跨所述 筒体的内径的方式设置在所述筒体内以拦截待经过所述筒体上的所述至少一个孔口排出的所述排出气体中的油。
  7. 根据权利要求5所述的涡旋压缩机，其中，所述截油装置在所述密封环上方一体地包围在所述筒体外侧。
  8. 根据权利要求5所述的涡旋压缩机，其中，所述至少一个孔口设置在所述筒体的侧壁上。
  9. 根据权利要求8所述的涡旋压缩机，其中，所述截油装置呈分体形式分别设置在所述筒体上的所述至少一个孔口中。
  10. 根据权利要求1至9中任一项所述的涡旋压缩机，其中，所述密封组件的所述顶端径向向内延伸超过所述隔板单元的中央通道的壁面，并且所述顶端的内边缘设置有在所述隔板单元的所述中央通道的壁面的径向内侧向上突出的突出部，其中，所述突出部与所述中央通道的壁面之间留有间隙以便接收从所述截油装置滴落的油的至少一部分。
  11. 根据权利要求4、7和9中任一项所述的涡旋压缩机，其中，所述密封环中设置有至少一个油孔，所述油孔的数量和位置设定成适于接收来自所述截油装置的油，并且所述油孔定位成在组装状态下位于所述密封部的径向内侧。
  12. 根据权利要求11所述的涡旋压缩机，其中，所述油孔为圆柱形通孔、倒锥形通孔或上端带有扩口部的通孔。
  13. 根据权利要求11所述的涡旋压缩机，其中，在所述密封环上设置有导油槽，所述导油槽位于所述油孔上方以用于接收从所述截油装置滴落的油并且将油引导到所述油孔中。
  14. 根据权利要求11所述的涡旋压缩机，其中，所述密封组件的所述顶端径向向内延伸超过所述隔板单元的中央通道的壁面，并且所述顶端的内边缘设置有在所述隔板单元的所述中央通道的壁面的径向内侧向上突出的突出部，其中，所述突出部与所述中央通道的壁面之间留有间隙以便接收从所述截油装置滴落的油的至少一部分。
  15. 根据权利要求14所述的涡旋压缩机，其中，所述密封组件的所述顶端上设置有位于所述第二密封面与所述突出部之间的凹槽，所述凹槽在组装状态下位于所述油孔下方，以接收来自所述油孔和所述间隙的油。
  16. 根据权利要求5至9中任一项所述的涡旋压缩机，其中，所述筒体构造为适于减小排气噪音的消音罩。
  17. 根据权利要求1至4中任一项所述的涡旋压缩机，其中，所述截油装置为带有滤网的过滤装置。
  18. 根据权利要求17所述的涡旋压缩机，其中，所述过滤装置为一体式过滤装置，所述过滤装置能够根据所述隔板单元的排气孔的布置适配成呈平板状、穹顶状、圆锥状或有顶筒状。
  19. 根据权利要求17所述的涡旋压缩机，其中，当所述隔板单元具有多个排气孔时，所述过滤装置为分别设置在所述隔板单元的排气孔处的分体式过滤装置。
  20. 根据权利要求17所述的涡旋压缩机，其中，所述截油装置为多层纺织纤维滤网或多层金属丝滤网。
  21. 根据权利要求1至9中任一项所述的涡旋压缩机，其中，所述密封组 件为设置在所述涡旋压缩机的定涡旋端板处的凹部中的浮动密封圈组件，并且所述顶端由所述浮动密封圈组件的上板提供。
  22. 根据权利要求1至9中任一项所述的涡旋压缩机，其中，所述第一密封面与所述第二密封面构成金属-金属密封。
PCT/CN2019/114652 2018-11-29 2019-10-31 具有密封-截油结构的涡旋压缩机 WO2020108224A1 (zh)

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