WO2016124120A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2016124120A1
WO2016124120A1 PCT/CN2016/073067 CN2016073067W WO2016124120A1 WO 2016124120 A1 WO2016124120 A1 WO 2016124120A1 CN 2016073067 W CN2016073067 W CN 2016073067W WO 2016124120 A1 WO2016124120 A1 WO 2016124120A1
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WO
WIPO (PCT)
Prior art keywords
boss
recess
pressure
fixed scroll
sealing member
Prior art date
Application number
PCT/CN2016/073067
Other languages
English (en)
French (fr)
Inventor
李洪山
戈大伟
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 CN201510055931.6A external-priority patent/CN105986996B/zh
Priority claimed from CN201520076138.XU external-priority patent/CN204610280U/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
Publication of WO2016124120A1 publication Critical patent/WO2016124120A1/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
    • 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

Definitions

  • the present invention relates to a scroll compressor.
  • a scroll compressor is increasingly used as compressors in refrigeration systems and HVAC systems due to their extremely efficient working capacity.
  • a scroll compressor includes an orbiting scroll member that meshes with a fixed scroll member to form a series of compression chambers. Rotation of the orbiting scroll member relative to the fixed scroll member causes the compression chamber to gradually decrease in size and cause the fluid dispensed into each chamber to be compressed.
  • the top of the fixed scroll member will be in three different pressure regions, ie, the outer circumference of the fixed scroll member is in the suction pressure region (ie, the low pressure side region), and the back pressure chamber of the fixed scroll member is at the intermediate pressure.
  • the side area and the exhaust port of the fixed scroll member are in the exhaust pressure region (ie, the high pressure side region).
  • the scroll compressor When the scroll compressor is in operation, the refrigerant therein is sucked from the low pressure side region, compressed, and discharged to the high pressure side region via the exhaust port, and the medium pressure side region provides back pressure during the compression of the refrigerant to set
  • the scroll member is pressed against the orbiting scroll member, however, if there is a leak between the three different pressure regions, the compressor performance is lowered, the exhaust gas temperature is increased, and the like. problem.
  • a sealing structure is employed between the three pressure zones to reduce or eliminate leakage between the three pressure zones.
  • the sealing structure used to isolate and seal the three pressure zones typically has a floating seal structure and a flat top seal structure.
  • the floating seal structure is sealed by a seal ring fixed by two metal plates, and the flat top seal structure is sealed by a spring-supported seal ring.
  • Another object of the present invention is to provide a scroll compressor which is less expensive to manufacture and less difficult to assemble.
  • a scroll compressor includes: a housing; a compression mechanism disposed in the housing, the compression mechanism Suitable for compressing a working fluid and comprising a fixed scroll member and a movable scroll member; a partition plate disposed in the housing and adjacent to the fixed scroll member, provided on a lower surface of the partition plate a first boss; a first extension of the first sealing member configured to abut a lower end surface of the first boss of the spacer and a second extension of the first sealing member a portion that is configured to abut against an annular wall of the first recess of the fixed scroll member to effect sealing, thereby separating a first pressure region having a different pressure within the housing from the second pressure region; and the first elastic member
  • the first elastic member is disposed in the first recess to hold the first sealing member against the first boss, wherein the fixed scroll member can be in a non-unloaded state Unloading status The first boss remains pressed against the first sealing member
  • Figure 1 is a longitudinal sectional view of a conventional scroll compressor
  • Figure 2 is a partial enlarged view of the sealing structure of the conventional scroll compressor shown in Figure 1;
  • Figure 3 is a schematic view of the dimensional relationship associated with the axial seal gap of the seal structure shown in Figure 2;
  • Figure 4 is a partial cross-sectional view showing a sealing structure of a scroll compressor according to a first embodiment of the present invention
  • Figure 5 is a schematic view of the dimensional relationship associated with the radial seal gap of the seal structure shown in Figure 4;
  • FIG. 6A to 6B are partial cross-sectional views showing the sealing structure of Fig. 4 when the fixed scroll members are in a non-unloaded state and an unloaded state, respectively;
  • Figure 7 is a partial cross-sectional view showing a sealing structure of a scroll compressor according to a second embodiment of the present invention.
  • Figure 8 is a partial enlarged cross-sectional view of the sealing structure of Figure 7.
  • a scroll compressor 100 (hereinafter sometimes referred to as a compressor) generally includes a housing 110.
  • the housing 110 may include a substantially cylindrical body 111, a top cover 112 disposed at one end of the body 111, and a bottom cover 114 disposed at the other end of the body 111.
  • the compressor 100 includes a compression mechanism disposed within the housing 110 that compresses the working fluid and includes a fixed scroll Component 150 and orbiting scroll member 160.
  • the compressor 100 further includes a partition 116 disposed within the housing 110 and adjacent to the fixed scroll member 150.
  • the partition 116 is disposed between the top cover 112 and the body 111 (in FIG.
  • a direction extends) to divide the internal space of the compressor into a high pressure side region and a low pressure side region (also referred to as a first pressure region or a third pressure region).
  • An intake joint 118 for sucking a fluid (also referred to as a working fluid), such as a gaseous refrigerant, is disposed in the low pressure side region, and an exhaust joint 119 for discharging the compressed fluid is disposed in the high pressure side region.
  • a motor 120 composed of a stator 122 and a rotor 124 is disposed in the housing 110.
  • a drive shaft 130 is disposed in the rotor 124 to drive the orbiting scroll member 160 to compress the working fluid between the fixed scroll member 150 and the orbiting scroll member 160.
  • the movable scroll member 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate 164, and a spiral blade 166 formed on the other side of the end plate 164.
  • the fixed scroll member 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate 154, and a recess 158 formed on the other side of the end plate 154.
  • An exhaust port 152 is formed at a substantially central position of the end plate 154. The space around the exhaust port 152 also constitutes a high pressure side region.
  • a series of compression chambers C1, C2, and C3 whose volume gradually decreases from the radially outer side to the radially inner side is formed between the spiral blade 156 of the fixed scroll member 150 and the spiral blade 166 of the movable scroll member 160.
  • the radially outermost compression chamber C1 is a low pressure chamber at the suction pressure
  • the radially innermost compression chamber C3 is a high pressure chamber at the exhaust pressure.
  • the intermediate compression chamber C2 is between the suction pressure and the discharge pressure, and is also referred to as a medium pressure chamber.
  • three different pressure chambers are formed inside the compression mechanism: a low pressure chamber, a medium pressure chamber, and a high pressure chamber.
  • One side of the movable scroll member 160 is supported by an upper portion (i.e., a support portion) of the main bearing housing 140, and one end of the drive shaft 130 is supported by a main bearing 144 provided in the main bearing housing 140.
  • the one end of the drive shaft 130 is provided with an eccentric crank pin 132, and an unloading bushing 142 is disposed between the eccentric crank pin 132 and the hub portion 162 of the movable scroll member 160.
  • the top end of the helical blade 156 of the scroll member 150 (also The distal end portion of the fixed scroll member is interposed between the end plate 164 of the orbiting scroll member 160 and the tip end of the spiral blade 166 of the orbiting scroll member 160 (also referred to as the distal end portion of the orbiting scroll member).
  • An axial seal is required between the end plates 154 of the scroll member 150.
  • a seal is also required between the partition 116 and the fixed scroll member 150.
  • a sealing structure S is usually provided in the recess of the fixed scroll member 150.
  • the sealing structure S of the conventional compressor will now be described in detail with reference to FIG. 2, and the sealing structure S is disposed between the partition 116 and the fixed scroll member 150.
  • the sealing structure S includes an outer sealing member S1, an outer spring S2, an inner sealing member S3, and an inner spring S4.
  • three different pressure regions are formed between the top of the fixed scroll member 150 and the lower portion of the partition 116: the low pressure side region LA, the medium pressure side region MA, and High pressure side area HA.
  • the space formed between the casing 110 below the partition 116 and the compression mechanism constitutes the low pressure side area LA between the exhaust hole of the top of the fixed scroll part 150 and the exhaust port 119 and the partition 116
  • the space formed constitutes the high pressure side region HA
  • the space formed between the recess 158 on the top of the fixed scroll member 150 and the lower portion of the partition 116 constitutes the intermediate pressure side region MA.
  • one purpose of providing the medium pressure side region MA is to provide back pressure to the fixed scroll member 150. Since one side of the movable scroll member 160 is supported by the support portion of the main bearing housing 140, the fixed scroll member 150 and the movable scroll member 160 can be effectively pressed together by the pressure in the intermediate pressure side region MA.
  • the state may be referred to as the non-unloaded state of the fixed scroll component 150.
  • the pressure in each compression chamber exceeds a set value
  • the resultant force generated by the pressure in these compression chambers will exceed the downward pressure provided in the medium pressure side region MA to cause the fixed scroll member 150 to move upward.
  • the fluid in the compression chamber will pass through the gap between the tip end of the spiral blade 156 of the fixed scroll member 150 and the end plate 164 of the movable scroll member 160 and the tip end and the fixed vortex of the spiral blade 166 of the movable scroll member 160.
  • the gap between the end plates 154 of the rotary member 150 leaks into the low pressure side region to effect unloading, thereby providing axial flexibility (also referred to as POP OFF) for the scroll compressor, also referred to as the fixed scroll member 150. Uninstall status.
  • the fixed scroll member 150 is axially moved upward by a certain overshoot distance (also referred to as POP OFF distance), hereinafter referred to as distance POP, and therefore, when the compressor 100 is operating normally ( That is, when the fixed scroll member 150 is in the non-unloading state, it is necessary to leave a certain gap C at least equal to or greater than the distance POP at the top of the partition 116 of the compressor 100 and the fixed scroll member 150 to prevent the provision of This axially flexible process occurs when the fixed scroll member 150 moves axially upwardly and ends with the end plate 116.
  • POP OFF distance a certain overshoot distance
  • the gap C reserved between the partition 116 and the top of the fixed scroll member 150 is less than the distance POP described above, in the process of providing such axial flexibility (ie, in the fixed scroll member 150)
  • the fixed scroll member 150 will collide with the diaphragm 116 to affect normal operation of the compressor 100 and even damage some components of the compressor 100.
  • This reserved clearance C is sealed by the outer seal member S1 and the inner seal member S3 during operation of the compressor 100.
  • the partition 116 may cause dimensional errors due to welding deformation during assembly into the housing 110, which is indicated by Tor 5 in FIG. 3, and Deformation due to pressure changes occurring during operation of compressor 100 results in dimensional errors, which are indicated by Tor 6 in Figure 3, which all result in a change in the distance between the top of fixed scroll member 150 and diaphragm 116.
  • the error is the sum of the tolerance bands composed of Tor 1 to Tor 6 .
  • the reserved gap C must also be at least greater than or equal to the distance POP.
  • the minimum thickness Tmin of the sealing member must be greater than the maximum gap Cmax of the reserved gap C, otherwise, the pressure acting of the sealing member in the medium pressure chamber MA or the high pressure chamber HA It is easy to be squeezed out or popped up.
  • C min minimum clearance reserved clearance C must be greater than the maximum distance from the POP POP max, otherwise, the fixed scroll member providing axial flexibility in process 150 will collide with the spacer 116.
  • the maximum gap C max of the reserved gap C is equal to the sum of the minimum gap C min of the reserved gap C plus the tolerance band composed of Tor 1 ⁇ Tor 6 . That is, when the design of the sealing member, the sealing member must be of a minimum thickness T min is greater than the maximum distance POP max plus a tolerance band composed of the sum and Tor 1 ⁇ Tor 6 thereof.
  • the distance POP in which the fixed scroll member 150 moves axially upward when the axial flexibility is provided, for example, in the case where a specific type of compressor requires a large POP distance, due to the minimum thickness of the sealing member
  • the relationship between T min and the maximum distance POP max and the tolerance band composed of Tor 1 to Tor 6 may cause the thickness of the sealing member to be excessively large, and the excessive thickness of the sealing member may affect the sealing performance, for example, the thickness of the sealing member Larger, it requires a large pressing force to press the edge of the sealing member against the partition plate and the fixed scroll member, and the pressure in the medium pressure side region does not reach the pressing force or even the high pressure side region.
  • the design of the sealing member of a suitable thickness is greatly limited by the above-described distance POP and the tolerance band composed of Tor 1 to Tor 6 .
  • the distance POP is usually fixed, so if the thickness of the sealing member is desired to be as thin as possible, the influence caused by the tolerance band composed of Tor 1 to Tor 6 must be reduced, in other words. It is necessary to reduce the errors constituting the tolerance zone, that is, it is necessary to improve the manufacturing precision of the components such as the fixed scroll member, the spacer, and the casing, and the assembly precision of these components, which also contributes to the manufacturing cost of the scroll compressor and Assembly presents higher requirements and challenges.
  • the sealing structure S100 of the scroll compressor of the first embodiment of the present invention will now be described with reference to FIGS. 4 to 6B, and the sealing structure S100 of the first embodiment and the sealing structure S of the prior art will be compared with reference to FIG.
  • FIG. 4 is a partial cross-sectional view showing a sealing structure of a scroll compressor of a first embodiment of the present invention
  • FIG. 5 is a schematic view showing a dimensional relationship related to a radial seal gap of the sealing structure shown in FIG. 6A to 6B are partial cross-sectional views of the sealing structure of Fig. 4 when the fixed scroll members are in a non-unloaded state and an unloaded state, respectively.
  • the sealing structure S100 of the scroll compressor includes a first sealing member S110.
  • the first sealing member S110 may be, for example, an outer sealing ring S110, and the first extending portion S111 of the outer sealing ring S110 is configured as Abutting against a lower end surface of the first boss 1161 on the lower surface of the partition 116 to achieve sealing, the second extension S112 of the outer seal S110 is configured to
  • the annular wall 157 of the first recess 158 of the fixed scroll member 150 in this embodiment, for example, can abut against the circumferential inner surface of the annular wall 157 to effect sealing, thereby providing different pressures within the scroll compressor
  • the first pressure zone is spaced apart from the second pressure zone.
  • the first pressure region and the second pressure region may be, for example, but not limited to, the low pressure side region LA and the medium pressure side region MA, respectively.
  • the sealing structure S100 further includes a first elastic member S120 disposed in the first recess 158 to hold the first sealing member S110 against the first boss 1161.
  • the fixed scroll member 150 is switchable between the non-unloading state and the unloading state, and when the fixed scroll member 150 is in the non-unloading state, the first boss 1161 remains pressed against the first sealing member S110 such that the first sealing member S110 is not subjected to the first
  • the pressure in the second pressure zone MA is extruded or ejected as shown in Figures 4 and 6A.
  • the fixed scroll member 150 When the fixed scroll member 150 is in the unloaded state, the first boss 1161 remains pressed against the first sealing member S110 and the lower end surface of the first boss 1161 is at least in the first recess 158 as shown in FIG. 6B. Wherein, the fixed scroll member 150 is moved upward by a distance POP in the axial direction with respect to the non-unloaded state in the unloaded state, as shown in FIG. 6B. It is to be noted that although the upper end surface of the annular wall 157 of the fixed scroll member 150 is spaced apart from the lower surface of the upper end surface of the end plate 116 facing the annular wall 157 in FIG. 6B, the distance may be It is close to zero as long as the upper end surface of the annular wall 157 does not contact the lower surface of the end plate 116.
  • the gap required to be sealed by the sealing member is converted from the axial gap C of the prior art to the radial gap Cr, as shown in FIG.
  • the radial gap Cr is a radial gap between the radially outer circumferential surface of the first boss 1161 and the radially inner circumferential surface of the first recess 158 of the fixed scroll member 150.
  • the setting of such radial clearance Cr is no longer affected and limited by the distance POP in which the fixed scroll member 150 moves axially upward when axial flexibility is provided, since it can be eliminated by adjusting the height of the first boss
  • the influence and limitation of the POP are distanced, and the height of the first boss does not affect and limit the thickness of the sealing member.
  • the thickness of the sealing member can be set as thin as possible to provide a better sealing effect
  • the sealing structure can also be disposed in a scroll compressor having a large distance POP, thereby ensuring a large distance POP.
  • the scroll compressor can achieve a better sealing effect.
  • the tolerance band composed of Tor 1r to Tor 4r needs to be considered, and in the aforementioned prior art, there is a seal.
  • the tolerance band consisting of Tor 1 to Tor 6 needs to be considered in the manufacture and assembly of the scroll compressor of the structure S.
  • the size ring (tolerance ring) that affects and limits such radial clearance Cr is relatively small, which helps to further reduce the thickness of the sealing member, thereby better improving the sealing performance.
  • this can also appropriately reduce the manufacturing precision and assembly accuracy of the scroll compressor while ensuring the sealing performance, thereby reducing the manufacturing cost of the entire scroll compressor and reducing the assembly difficulty.
  • the sealing member is less likely to be ejected during the assembly of the compressor, so that the sealing member can be effectively prevented from being ejected during the assembly process.
  • the sealing structure S100 of the scroll compressor may further include a second sealing member S130, which in the present embodiment may be, for example, an inner seal S130, a first extension S131 of the inner seal S130 Abutting against a lower end surface of the second boss 1162 on the lower surface of the partition 116 to achieve sealing, the second extension S132 of the inner seal S130 is configured to abut against the annular wall 159 of the fixed scroll member 150, in the present embodiment
  • the third pressure region can be, for example It is, but not limited to, the high pressure side region HA.
  • the sealing structure S100 further includes a second elastic member S140 disposed in the second recess 152 of the fixed scroll member 150 to hold the second sealing member S130 against the second boss 1162.
  • a second elastic member S140 disposed in the second recess 152 of the fixed scroll member 150 to hold the second sealing member S130 against the second boss 1162.
  • the second recessed portion 152 may be the above-described exhaust port, but may be a recess different from the above-described exhaust port.
  • the above arrangement of the sealing structure 200 can also achieve the same advantages as the above-described advantages of the sealing structure 100, and thus will not be described in detail herein.
  • the sealing structure 100 can be combined with a sealing structure of the prior art, for example before The described sealing structure S (sealing the axial gap) is used in combination, or the sealing structure 200 can be used in combination with a sealing structure of the prior art, such as the previously described sealing structure S, ie, the sealing structure 100
  • the sealing structure 200 is used to seal the high pressure side region HA and the medium pressure side region MA, and the sealing structure S used in combination is used to seal the medium pressure side region MA and the low pressure side region LA, or the sealing structure 100 is to be sealed.
  • the sealing structure 200 is used to seal the low pressure side area LA and the medium pressure side area MA
  • the sealing structure S used in combination is used to seal the medium pressure side area MA and the high pressure side area HA.
  • the lower end surface of the first boss 1161 is in the first recess 158 or substantially flush with the upper end surface of the annular wall 157 of the first recess 158, and the second boss 1261 The lower end surface is in the second recess 258 or substantially flush with the upper end surface of the annular wall 159 of the second recess 258.
  • the lower end surface of the first boss 1161 is higher in the axial direction than the upper end surface of the annular wall 157 of the first recess 158 by the thickness of the first sealing member S110
  • About half of the lower end surface of the second boss 1261 is substantially half the thickness of the second sealing member S130 in the axial direction than the upper end surface of the annular wall 159 of the second recess 258.
  • the lower end surface of the first boss 1161 and the lower end surface of the second boss 1162 are substantially on the same horizontal surface, as shown in FIG. 4, but the lower end surface of the first boss 1161 and the lower end surface of the second boss 1162 may also be They are at different levels of height.
  • the upper end surface of the annular wall 157 of the first recess 158 and the upper end surface of the annular wall 159 of the second recess 152 may also be substantially at the same level as shown in FIG.
  • the lower end surface of the first boss 1161 and the lower end surface of the second boss 1162 are substantially on the same horizontal plane and the upper end surface of the annular wall 159 of the first recess 158 and the annular wall 159 of the second recess 152 The end faces are also roughly on the same level.
  • the distance from the upper end surface of the annular wall 157 of the first recess 158 in the axial direction from the lower surface of the partition 116 facing the upper end surface of the annular wall 157 of the first recess 158 is designed such that when the fixed scroll member 150 is at In the unloaded state, the fixed scroll member 150 is not in contact with the partition 116.
  • the upper end surface of the annular wall 159 of the second recess 152 is disposed in the axial direction from the lower surface of the partition 116 facing the upper end surface of the annular wall 159 of the second recess 152 such that when the fixed scroll member 150 is at In the unloaded state, the fixed scroll member 150 is not in contact with the partition 116.
  • first extension S111 and the second extension S112 of the first sealing member S110 are integrally formed and the first sealing member S110 has a substantially L-shaped cross section, and a first extension S111 and a second extension S112 may be formed.
  • the radial distance between the radially outer circumferential surface of the first boss 1161 of the partition 116 and the radially inner circumferential surface of the annular wall 157 of the first recess 158 of the fixed scroll member 150 is less than or equal to that of the first sealing member S110 Thickness, as shown schematically in Figure 4.
  • first extension S131 and the second extension S132 of the second sealing member S130 are integrally formed and the second sealing member S130 has a substantially L-shaped cross section, and the first extension S131 and the second extension S132 may be formed.
  • the radial distance between the radially outer circumferential surface of the second boss 1261 of the partition 116 and the radially inner circumferential surface of the annular wall 159 of the second recess 258 of the fixed scroll member 150 is less than or equal to that of the second sealing member S130 thickness.
  • first elastic member S120 may be a coil spring that provides an axial compressive load to the first sealing member S110.
  • the second elastic member S140 may also be a coil spring that provides an axial compressive load to the second sealing member S130.
  • first elastic member S120 and the second elastic member S140 are not limited to the coil spring as long as it can hold the first sealing member S110 or the second sealing member S130 against the first boss 1161 or the second boss 1261, can.
  • FIG. 7 is a partial cross-sectional view showing a sealing structure of a scroll compressor according to a second embodiment of the present invention
  • Fig. 8 is a partially enlarged cross-sectional view showing the sealing structure of Fig. 7.
  • the second embodiment is different from the first embodiment in the configuration of the boss of the spacer and the configuration of the recess of the fixed scroll member, and thus in the second embodiment, these differences will be mainly described, and will be omitted. Descriptions of the same components as those of the first embodiment.
  • the first of the partitions 216 The radially outer circumferential surface of the boss 2161 is substantially parallel to the radially inner circumferential surface of the first recess 258 of the fixed scroll member, for example, the radially inner circumferential surface of the annular wall 257 of the first recess 258, as shown in FIG.
  • the radially outer circumferential surface of the first boss 2161 is tapered downward in the axial direction, and the radially outer circumferential surface of the first boss 2161 forms a first angle with respect to a plane in which the lower end surface of the first boss 2161 is located ⁇ , the first angle ⁇ is equal to or less than 90° as shown in FIG.
  • the first angle ⁇ is equal to 90°, the first boss 2161 and the first recess 258 become the first boss 1161 and the first recess 158 in the first embodiment.
  • the radially outer circumferential surface of the first boss 2161 of the partition 216 and the radially inner circumferential surface of the first recess 258 of the fixed scroll member for example, the radially inner circumferential surface of the annular wall 257 of the first recess 258
  • the radial distance is less than or equal to the thickness of the first sealing member S110.
  • the radially inner circumferential faces are substantially parallel as shown in FIG.
  • the radially outer peripheral surface of the second boss 2162 is tapered downward in the axial direction, and the radially outer peripheral surface of the second boss 2162 forms a second angle with respect to the plane in which the lower end surface of the second boss 2162 is located
  • the second angle is equal to or less than 90° as shown in FIG.
  • the second boss 2162 and the second recess 252 become the second boss 1162 and the second recess 152 in the first embodiment.
  • the radially outer circumferential surface of the second boss 2162 of the partition 216 and the radially inner circumferential surface of the second recess 252 of the fixed scroll member for example, the radially inner circumferential surface of the annular wall 259 of the first recess 252
  • the radial distance is less than or equal to the thickness of the second sealing member S130.
  • the gap required to be sealed by the sealing member is converted from the axial gap of the prior art to the radial gap, and the setting of the radial gap is not It is again affected and limited by the distance POP in which the fixed scroll member moves axially upward when axial flexibility is provided.
  • the thickness of the sealing member can be set as thin as possible to provide a better sealing effect, and in addition, the sealing structure can also be disposed in a scroll compressor having a large distance POP, thereby ensuring a large distance POP. The scroll compressor can achieve a better sealing effect.
  • the size ring (tolerance ring) that affects and limits such radial clearance is relatively small, This helps to further reduce the thickness of the sealing member, thereby improving the sealing performance. In addition, this can also appropriately reduce the manufacturing precision and assembly accuracy of the scroll compressor while ensuring the sealing performance, thereby reducing the manufacturing cost of the entire scroll compressor and reducing the assembly difficulty. Further, in the scroll compressor having such a sealing structure, the sealing member is less likely to be ejected during the assembly of the compressor, so that the sealing member can be effectively prevented from being ejected during the assembly process.
  • a second boss is further disposed on a lower surface of the separator, and the scroll compressor further includes: a second sealing member, the first extension of the second sealing member is configured to abut a lower end surface of the second boss of the spacer and a second extension of the second sealing member configured to abut against an annular wall of the second recess of the fixed scroll member to effect sealing
  • the second pressure region is spaced apart from the third pressure region within the housing, wherein the pressure in the third pressure region is different than the pressure in the first pressure region and the second pressure region; and second An elastic member disposed in the second recess to hold the second sealing member against the second boss, wherein when the fixed scroll member is in the In the non-unloading state, the second boss remains pressed against the second sealing member such that the second sealing member is not subjected to a pressure greater in the second pressure region and the third pressure region Pressure extrusion or ejection in the area, when stated When the rotary member is in the unloaded state, the second boss of the holding member pressed against the second
  • first boss and the second boss are arranged in such a manner that one is located radially inward of the other, or the first sealing member and the second sealing member are located one by one One is arranged radially inwardly.
  • the lower end surface of the first boss is in the first recess or on the annular wall of the first recess
  • the end faces are generally flush.
  • the lower end surface of the first boss is higher in the axial direction than the upper end surface of the annular wall of the first recess About half of the thickness of the first sealing member is described.
  • the lower end surface of the second boss and the lower end surface of the first boss are substantially on the same horizontal plane and/or the upper end surface of the annular wall of the second recess and the The upper end faces of the annular walls of the first recess are substantially at the same level.
  • a radially outer circumferential surface of the first boss is substantially parallel to a radially inner circumferential surface of the annular wall of the first recess.
  • the radially outer peripheral surface of the first boss is tapered downward in the axial direction, and the radially outer peripheral surface of the first boss is opposite to the lower end face of the first boss
  • the plane in which it forms forms a first angle, the first angle being equal to or less than 90°.
  • a radial distance between a radially outer circumferential surface of the first boss and a radially inner circumferential surface of the first recess is less than or equal to a thickness of the first sealing member.
  • a radially outer circumferential surface of the second boss is substantially parallel to a radially outer circumferential surface of the first boss
  • a radially inner circumferential surface of the annular wall of the second recess is substantially parallel to A radially inner circumferential surface of the annular wall of the first recess.
  • a radial distance between a radially outer circumferential surface of the second boss and a radially inner circumferential surface of the second recess is less than or equal to a thickness of the second sealing member.
  • the distance between the upper end surface of the annular wall of the first recess and the lower surface of the partition facing the upper end surface of the annular wall of the first recess in the axial direction is designed The fixed scroll member is not in contact with the partition when the fixed scroll member is in the unloaded state.
  • the distance between the upper end surface of the annular wall of the second recess and the lower surface of the partition facing the upper end surface of the annular wall of the second recess in the axial direction is designed The fixed scroll member is not in contact with the partition when the fixed scroll member is in the unloaded state.
  • first extension and the second extension of the first sealing member are integrally formed and the first sealing member has a substantially L-shaped cross section and/or the second sealing member
  • first extension portion and the second extension portion are integrally formed and the second sealing member has a substantially L-shaped cross section.
  • the first pressure region corresponds to a low pressure side region in communication with intake pressure and the second pressure region corresponds to a series of compression chambers formed between the orbiting scroll member and the fixed scroll member a medium pressure side region in which one of the compression chambers communicates, or the first pressure region corresponds to a high pressure side region in communication with the exhaust pressure and the second pressure region corresponds to An intermediate pressure side region in which one of the series of compression chambers formed between the orbiting scroll member and the fixed scroll member communicates with the compression chamber.

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Abstract

一种涡旋压缩机(100)，包括：壳体(110)；包括定涡旋部件(150)和动涡旋部件(160)的压缩机构(150,160)；设置在壳体(110)内且邻近定涡旋部件(150)的隔板(116，216)，在隔板(116，126)的下表面上设置有第一凸台(1161，2161)；第一密封构件(S110)，其第一延伸部(S111)构造成抵靠隔板(116，216)的第一凸台(1161，2161)的下端面并且其第二延伸部(S112)构造成抵靠定涡旋部件(150)的第一凹部(158，258)的环形壁(157，257)实现密封，以将壳体(110)内的第一压力区域与第二压力区域隔开；第一弹性构件(S120)，其设置在第一凹部(158，258)中以将第一密封构件(S110)保持压靠在第一凸台(1161，2161)上，定涡旋部件(150)能够在非卸载状态与卸载状态之间转换，当定涡旋部件(150)处于非卸载状态时，第一凸台(1161，2161)保持压靠第一密封构件(S110)使得第一密封构件(S110)不会被压力区域中的压力挤出或弹出，当定涡旋部件(150)处于卸载状态时，第一凸台(1161，2161)保持压靠第一密封构件(S110)并且其下端面至少处在第一凹部(158，258)中。

Description

涡旋压缩机
相关申请的交叉引用
本申请要求2015年2月3日提交中国专利局、申请号分别为201510055931.6和No.201520076138.X的中国专利申请的优先权，其全部内容通过引用结合到本申请中。
技术领域
本发明涉及一种涡旋压缩机。
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。
由于涡旋压缩机具有极高效的工作能力，因而涡旋压缩机日益普遍地用作制冷系统和HVAC系统中的压缩机。通常地，涡旋压缩机包括与定涡旋部件彼此啮合的动涡旋部件以形成一系列的压缩腔。动涡旋部件相对于定涡旋部件的旋转使压缩腔的尺寸逐渐减小并导致分配到每个腔内的流体被压缩。
在涡旋压缩机的一系列压缩腔中存在径向最外侧的处于吸气压力的低压腔、径向最内侧的处于排气压力的高压腔、腔内压力处于吸气压力与排气压力之间的中压腔。在定涡旋部件的端板的一侧设置有凹部，该凹部与隔板配合形成大致封闭的腔室，该腔室与中压腔流体连通从而形成为定涡旋部件提供背压的背压腔。这样，定涡旋部件的顶部会处于三种不同的压力区域中，即，定涡旋部件的外周处于吸气压力区(即，低压侧区域)、定涡旋部件的背压腔处于中压侧区域以及定涡旋部件的排气口处于排气压力区域(即，高压侧区域)。
涡旋压缩机在运行时，其内的制冷剂从低压侧区域吸入、经过压缩后经由排气口排出高压侧区域，且在制冷剂压缩的过程中该中压侧区域提供背压以将定涡旋部件朝向动涡旋部件压靠，然而，如果这三个不同的压力区域之间存在泄漏，则会导致压缩机性能降低、排气温度升高等 问题。为此，在这三个压力区域之间采用了密封结构，以减小或消除这三个压力区域之间的泄漏。用来隔离和密封这三个压力区域的密封结构通常有浮动密封圈结构和平顶密封圈结构。浮动密封圈结构通过由两块金属板固定的密封圈来实现密封，平顶密封圈结构通过由弹簧支撑的密封圈来实现密封。
然而，仍然存在对于改进密封结构的密封性能、降低涡旋压缩机的制造成本或降低涡旋压缩机的装配难度等方面的需求。
发明内容
本发明的一个目的是提供一种能够使压缩机内不同压力区域之间密封性能显著改进的涡旋压缩机。
本发明的又一个目的是提供一种适应更大上冲距离的涡旋压缩机。
本发明的另一个目的是提供一种制造成本更低、装配难度降低的涡旋压缩机。
为了实现上述目的中的一个或多个目的，根据本发明实施方式的一个方面，提供了一种涡旋压缩机，其包括：壳体；设置在所述壳体内的压缩机构，所述压缩机构适于压缩工作流体并且包括定涡旋部件和动涡旋部件；隔板，所述隔板设置在所述壳体内并且邻近所述定涡旋部件，在所述隔板的下表面上设置有第一凸台；第一密封构件，所述第一密封构件的第一延伸部构造成抵靠所述隔板的所述第一凸台的下端面并且所述第一密封构件的第二延伸部构造成抵靠所述定涡旋部件的第一凹部的环形壁以实现密封，从而将所述壳体内的具有不同压力的第一压力区域与第二压力区域隔开；以及第一弹性构件，所述第一弹性构件设置在所述第一凹部中，以将所述第一密封构件保持压靠在所述第一凸台上，其中，所述定涡旋部件能够在非卸载状态与卸载状态之间转换，当所述定涡旋部件处于所述非卸载状态时，所述第一凸台保持压靠所述第一密封构件使得所述第一密封构件不会被所述第一压力区域和所述第二压力区域中压力较大的一个压力区域中的压力挤出或弹出，当所述定涡旋部件处于所述卸载状态时，所述第一凸台保持压靠所述第一密封构件并且所述第一凸台的所述下端面至少处在所述第一凹部中。
附图说明
通过以下参照附图的描述，本发明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发明的范围，附图并非按比例绘制，并且一些特征可能被放大或缩小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2是图1中所示的常规的涡旋压缩机的密封结构的局部放大视图；
图3是图2中所示的与密封结构的轴向密封间隙相关的尺寸关系的示意性视图；
图4是本发明的第一实施方式的涡旋压缩机的密封结构的局部剖视图；
图5是图4中所示的与密封结构的径向密封间隙相关的尺寸关系的示意性视图；
图6A至图6B示出了图4中的密封结构在定涡旋部件分别处于非卸载状态和卸载状态时的局部剖视图；
图7是本发明的第二实施方式的涡旋压缩机的密封结构的局部剖视图；
图8是图7中的密封结构的局部放大剖视图。
具体实施方式
下面对本发明各实施方式的描述仅仅是示例性的，而绝不是对本发明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描述常规的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(下文中有时也会称作压缩机)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111一端的顶盖112以及设置在本体111另一端的底盖114。压缩机100包括设置在壳体110内的压缩机构，该压缩机构压缩工作流体并且包括定涡旋 部件150和动涡旋部件160。压缩机100还包括隔板116，隔板116设置在壳体110内并且邻近定涡旋部件150，例如，隔板116设置在顶盖112与本体111之间(在图1中为沿大致水平的方向延伸)以将压缩机的内部空间分隔成高压侧区域和低压侧区域(二者也称作第一压力区域或第三压力区域)。在低压侧区域设置有用于吸入流体(也称作工作流体)、比如气态制冷剂的进气接头118，在高压侧区域设置有用于排出压缩后的流体的排气接头119。壳体110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以驱动动涡旋部件160，从而压缩定涡旋部件150与动涡旋部件160之间的工作流体。动涡旋部件160包括端板164、形成在端板164一侧的毂部162以及形成在端板164另一侧的螺旋状的叶片166。定涡旋部件150包括端板154、形成在端板154一侧的螺旋状的叶片156以及形成在端板154另一侧的凹部158。在端板154的大致中央位置处形成有排气口152。排气口152周围的空间也构成高压侧区域。在定涡旋部件150的螺旋叶片156与动涡旋部件160的螺旋叶片166之间形成一系列体积从径向外侧向径向内侧逐渐减小的压缩腔C1、C2和C3。其中，径向最外侧的压缩腔C1为处于吸气压力的低压腔，径向最内侧的压缩腔C3为处于排气压力的高压腔。中间的压缩腔C2处于吸气压力与排气压力之间，从而也被称作中压腔。由此，在压缩机构的内部形成了三种不同的压力腔：低压腔、中压腔以及高压腔。
动涡旋部件160的一侧由主轴承座140的上部(即支撑部)支撑，驱动轴130的一端由设置在主轴承座140中的主轴承144支撑。驱动轴130的所述一端设置有偏心曲柄销132，在偏心曲柄销132与动涡旋部件160的毂部162之间设置有卸载衬套142。通过马达120的驱动，动涡旋部件160将相对于定涡旋部件150平动转动(即，动涡旋部件160的中心轴线绕定涡旋部件150的中心轴线旋转，但是动涡旋部件160本身不会绕自身的中心轴线旋转)以实现流体的压缩。上述平动转动是通过定涡旋部件150与动涡旋部件160之间设置的十字滑环180来实现的。经过定涡旋部件150和动涡旋部件160压缩后的流体通过排气口152排出到高压侧区域。为了防止高压侧区域的流体在特定情况下经由排气口152回流到低压侧区域，可以在排气口152处设置单向阀或排气阀(未示出)。
为了实现流体的压缩，定涡旋部件150的螺旋叶片156的顶端(也 称作定涡旋部件的远端部)与动涡旋部件160的端板164之间以及动涡旋部件160的螺旋叶片166的顶端(也称作动涡旋部件的远端部)与定涡旋部件150的端板154之间需要轴向密封。另外，隔板116与定涡旋部件150之间也需要密封。为此，通常在定涡旋部件150的凹部中设置密封结构S。
现在结合图2详细描述现有压缩机的密封结构S，密封结构S设置在隔板116与定涡旋部件150之间。密封结构S包括外密封构件S1、外弹簧S2、内密封构件S3和内弹簧S4。当密封结构S安装在涡旋压缩机100中时，在定涡旋部件150的顶部与隔板116的下部之间形成了三个不同的压力区域：低压侧区域LA、中压侧区域MA和高压侧区域HA。其中，由隔板116下方的壳体110和压缩机构之间所形成的空间构成低压侧区域LA，由定涡旋部件150顶部的连通到排气接头119的排气孔和隔板116之间所形成的空间构成高压侧区域HA，而由定涡旋部件150的顶部上的凹部158和隔板116的下部之间所形成的空间构成中压侧区域MA。本领域技术人员可以理解的是，提供中压侧区域MA的一个目的是为了对定涡旋部件150提供背压。由于动涡旋部件160的一侧由主轴承座140的支撑部支撑，所以利用中压侧区域MA中的压力可以有效地将定涡旋部件150和动涡旋部件160压在一起，这种状态可以称作定涡旋部件150的非卸载状态。当各个压缩腔中的压力超过设定值时，这些压缩腔中的压力所产生的合力将超过中压侧区域MA中提供的下压力从而使得定涡旋部件150向上运动。此时，压缩腔中的流体将通过定涡旋部件150的螺旋叶片156的顶端与动涡旋部件160的端板164之间的间隙以及动涡旋部件160的螺旋叶片166的顶端与定涡旋部件150的端板154之间的间隙泄漏到低压侧区域以实现卸载，从而为涡旋压缩机提供了轴向柔性(也称作POP OFF)，这种状态也称作定涡旋部件150的卸载状态。
对于密封结构S而言，外密封构件S1和内密封构件S3的轴向位移受到隔板116的限制。在提供这种轴向柔性的过程中定涡旋部件150轴向向上移动了一定的上冲距离(也称作POP OFF距离)，以下简称为距离POP，因此，在压缩机100正常运行时(即，在定涡旋部件150处于非卸载状态时)，需要在压缩机100的隔板116与定涡旋部件150的顶部留有至少大于或等于该距离POP的一定间隙C，以防止在提供这种轴向柔性的过程中定涡旋部件150轴向向上移动时与端板116发生干 涉，换句话说，如果隔板116与定涡旋部件150的顶部之间预留的间隙C小于上述距离POP，则在提供这种轴向柔性的过程中(即，在定涡旋部件150处于卸载状态时)定涡旋部件150将与隔板116发生碰撞进而影响压缩机100的正常运行甚至损坏压缩机100的一些部件。在压缩机100的运行过程中，这种预留间隙C由外密封构件S1和内密封构件S3进行密封。
参照图3详细描述压缩机中与预留间隙C(轴向密封间隙)相关的尺寸关系，在压缩机100的制造及组装过程中，存在如下制造误差：定涡旋部件150的顶部的上端面距定涡旋部件150下端面之间的距离、即定涡旋部件150的轴向高度在制造过程中存在的制造误差，其在图3中由Tor1表示；动涡旋部件160的与定涡旋部件150下端面配合的上端面距动涡旋部件160的与主轴承座140的止推表面配合的下端面之间的距离在制造过程中存在的误差，其在图3中由Tor2表示；本体111的与隔板116接触的上端面距本体111底部的距离、即本体111的轴向高度在制造过程中存在的制造误差，其在图3中由Tor3表示；隔板116的与密封构件接触的下表面距隔板116与本体111接触的端面之间的距离在制造过程中存在的误差，其在图3中由Tor4表示。
另外，在压缩机100的组装和运行过程中，隔板116在组装到壳体110的过程中会因焊接变形而产生尺寸误差，其在图3中由Tor5表示，而且，隔板也会因为压缩机100运行过程中产生的压力变化而发生变形从而产生尺寸误差，其在图3中由Tor6表示，这些都会导致定涡旋部件150的顶部与隔板116之间的距离发生变化。
压缩机100中的多种部件在制造过程中存在的误差以及隔板116的上述变形产生的尺寸误差、即Tor1～Tor6使得在设定预留间隙C时必须考虑这些尺寸误差，这些尺寸误差为Tor1～Tor6组成的公差带之和。除此之外，这种预留间隙C还必须至少大于或等于距离POP。
因此，为了确保密封构件将预留间隙C完全密封，密封构件的最小厚度Tmin必须大于预留间隙C的最大间隙Cmax，否则，密封构件在中压腔MA或高压腔HA中的压力作用下很容易被挤出或弹出。另外，预留间隙C的最小间隙Cmin必须大于距离POP的最大距离POPmax，否则，在提供轴向柔性的过程中定涡旋部件150将与隔板116发生碰撞。其中，预留间隙C的最大间隙Cmax等于预留间隙C的最小间隙Cmin加上 Tor1～Tor6组成的公差带之和构成的总和。也就是说，在设计密封构件时，必须使密封构件的最小厚度Tmin大于最大距离POPmax加上Tor1～Tor6组成的公差带之和构成的总和。
然而，在提供轴向柔性时定涡旋部件150轴向向上移动的距离POP较大的情况下，例如，在特定类型的压缩机需要较大的POP距离的情况下，由于密封构件的最小厚度Tmin与最大距离POPmax以及Tor1～Tor6组成的公差带之间的关系，会导致密封构件的厚度过大，而密封构件的厚度过大则会影响密封性能，比如，密封构件厚度过大则需要极大的按压力将密封构件的边缘压靠于隔板和定涡旋部件上，而在中压侧区域中的压力达不到这种按压力的情况下、甚至高压侧区域中的压力也达不到这种按压力的情况下会导致密封构件的边缘不能紧靠于隔板和定涡旋部件，这进而会导致压缩流体从密封构件的边缘泄漏从而影响密封性能。因此，对于适当厚度密封构件的设计极大地受到了上述距离POP以及由Tor1～Tor6组成的公差带的限制。
对于某一类型的涡旋压缩机而言，距离POP通常是固定的，因此，如果希望密封构件的厚度尽量较薄，则必须减小由Tor1～Tor6组成的公差带造成的影响，换言之，必须减小构成公差带的各误差，即，必须提高定涡旋部件、隔板以及壳体等部件的制造精度以及这些部件的装配精度，而这也对涡旋压缩机的制造成本及其装配提出了更高的要求和挑战。
现在参照图4至图6B描述本发明的第一实施方式的涡旋压缩机的密封结构S100，并参照图5比较第一实施方式的密封结构S100与现有技术的密封结构S。
图4示出了本发明的第一实施方式的涡旋压缩机的密封结构的局部剖视图，图5示出了图4中所示的与密封结构的径向密封间隙相关的尺寸关系的示意性视图，图6A至图6B示出了图4中的密封结构在定涡旋部件分别处于非卸载状态和卸载状态时的局部剖视图。
参照图4，涡旋压缩机的密封结构S100包括第一密封构件S110，该第一密封构件S110在本实施方式中例如可以为外密封圈S110，外密封圈S110的第一延伸部S111构造成抵靠隔板116的下表面上的第一凸台1161的下端面以实现密封，外密封圈S110的第二延伸部S112构造成 抵靠定涡旋部件150的第一凹部158的环形壁157、在本实施方式中例如可以抵靠环形壁157的周向内表面以实现密封，从而将涡旋压缩机内的具有不同压力的第一压力区域与第二压力区域隔开。在本实施方式中，第一压力区域和第二压力区域例如可以分别为但不限于低压侧区域LA和中压侧区域MA。密封结构S100还包括第一弹性构件S120，第一弹性构件S120设置在第一凹部158中，以将第一密封构件S110保持压靠在第一凸台1161上。定涡旋部件150能够在非卸载状态与卸载状态转换，当定涡旋部件150处于非卸载状态时，第一凸台1161保持压靠第一密封构件S110使得第一密封构件S110不会被第二压力区域MA中的压力挤出或弹出，如图4和图6A所示。当定涡旋部件150处于卸载状态时，第一凸台1161保持压靠第一密封构件S110并且第一凸台1161的下端面至少处在第一凹部158中，如图6B所示。其中，定涡旋部件150在卸载状态时相对于在非卸载状态沿轴向方向向上移动了距离POP，如图6B所示。需要指出的是，尽管在图6B中定涡旋部件150的环形壁157的上端面与端板116的面对环形壁157的所述上端面的下表面隔开一定距离，但是这种距离可以接近于零只要环形壁157的上端面不接触端板116的该下表面即可。
在第一实施方式中，通过密封结构S100的这种布置，使得需要由密封构件进行密封的间隙由现有技术的轴向间隙C转换为径向间隙Cr，如图5所示，需要进行密封的该径向间隙Cr为第一凸台1161的径向外周面与定涡旋部件150的第一凹部158的径向内周面之间的径向间隙。而这种径向间隙Cr的设定不再受到在提供轴向柔性时定涡旋部件150轴向向上移动的距离POP的影响和限制，这是因为可以通过调节第一凸台的高度来消除距离POP的影响和限制，而第一凸台的高度并不影响和限制密封构件的厚度。这样，可以将密封构件的厚度设定为尽可能薄从而提供更佳的密封效果，另外，这种密封结构还可以设置在具有距离POP较大的涡旋压缩机中，从而确保距离POP较大的涡旋压缩机可以获得更佳的密封效果。
在具有这种密封结构S100的涡旋压缩机的制造和组装过程中，需要考虑如下制造和组装误差：隔板116的径向外周面距隔板116的中心的距离、即隔板116的半径的制造误差Tor1r；定涡旋部件150的中心相对于隔板116的中心的距离、即二者之间的组装误差Tor2r；定涡旋部件150的第一凹部158的环形壁157的径向内表面距定涡旋部件150的中心的距离、即第一凹部158的径向内表面的半径的制造误差Tor3r； 第一凸台1161的径向外周面距隔板116的径向外周面之间的距离、即第一凸台1161的径向外周面的制造误差Tor4r，如图5所示。
也就是说，在具有这种密封结构S100的涡旋压缩机的制造和组装过程中，仅需要考虑由Tor1r～Tor4r组成的公差带，而在前面提到的现有技术中的具有密封结构S的涡旋压缩机的制造和组装过程中需要考虑由Tor1～Tor6组成的公差带。可见，影响和限制这种径向间隙Cr的尺寸环(公差环)相对较少，这有助于进一步地降低密封构件的厚度，从而更好地提升密封性能。另外，这也可以在保证密封性能的同时适当地降低涡旋压缩机的制造精度和组装精度，从而可以降低整个涡旋压缩机的制造成本并且降低装配难度。此外，在具有这种密封结构S100的涡旋压缩机中，密封构件在压缩机装配的过程中不易弹出，从而能够有效地防止密封构件在装配过程中弹出。
优选地，涡旋压缩机的密封结构S100还可以包括第二密封构件S130，该第二密封构件S130在本实施方式中例如可以为内密封圈S130，内密封圈S130的第一延伸部S131构造成抵靠隔板116的下表面上的第二凸台1162的下端面以实现密封，内密封圈S130的第二延伸部S132构造成抵靠定涡旋部件150的环形壁159、在本实施方式中例如可以抵靠环形壁159的周向内表面以实现密封，从而将涡旋压缩机内的第二压力区域与第三压力区域隔开，在该实施方式中，第三压力区域例如可以为但不限于高压侧区域HA。密封结构S100还包括第二弹性构件S140，第二弹性构件S140设置在定涡旋部件150的第二凹部152中，以将第二密封构件S130保持压靠在第二凸台1162上。当定涡旋部件150处于非卸载状态时，第二凸台1162保持压靠第二密封构件S130使得第二密封构件S130不会被第三压力区域中的压力挤出或弹出，当定涡旋部件150处于卸载状态时，第二凸台1162保持压靠第二密封构件S130并且第二凸台1162的下端面至少处在第二凹部152中。
另外，该第二凹部152可以是上述排气口，但也可以是不同于上述排气口的凹部。
在本实施方式中，密封结构200的上述布置同样能够获得与密封结构100的上述优点相同的优点，因此这里不再详细描述。
另外，可以将密封结构100与现有技术中的一种密封结构、例如之前 描述的密封结构S(对轴向间隙进行密封)结合使用，或者，可以将密封结构200与现有技术中的一种密封结构、例如之前描述的密封结构S结合使用，即，将密封结构100或密封结构200用于对高压侧区域HA和中压侧区域MA进行密封，而将结合使用的密封结构S用于对中压侧区域MA和低压侧区域LA进行密封，或者，将密封结构100或密封结构200用于对低压侧区域LA和中压侧区域MA进行密封，而将结合使用的密封结构S用于对中压侧区域MA和高压侧区域HA进行密封。这些将本实施方式与现有技术结合使用的方案同样能够获得单独使用密封结构100或密封结构200所能够实现的优点。然而，将密封结构200的上述布置与密封结构100的上述布置结合使用可以获得更优的效果，即，能够同时获得高压侧区域HA、中压侧区域MA以及低压侧区域LA三者之间的最优密封效果、更大限度地降低压缩机的制造成本以及使压缩机更容易地装配。
当定涡旋部件150处于非卸载状态时，第一凸台1161的下端面处在第一凹部158中或者与第一凹部158的环形壁157的上端面大致齐平，第二凸台1261的下端面处在第二凹部258中或者与第二凹部258的环形壁159的上端面大致齐平。
替代性地，当定涡旋部件150处于非卸载状态时，第一凸台1161的下端面在轴向方向上比第一凹部158的环形壁157的上端面至多高第一密封构件S110的厚度的大致一半，第二凸台1261的下端面在轴向方向上比第二凹部258的环形壁159的上端面至多高第二密封构件S130的厚度的大致一半。
第一凸台1161的下端面和第二凸台1162的下端面大致处在同一水平面上，如图4所示，但是第一凸台1161的下端面和第二凸台1162的下端面也可以分别处在不同高度的水平面上。或者，第一凹部158的环形壁157的上端面和第二凹部152的环形壁159的上端面也可以大致处在同一水平面上，如图4所示。替代性地，第一凸台1161的下端面和第二凸台1162的下端面大致处在同一水平面上并且第一凹部158的环形壁159的上端面和第二凹部152的环形壁159的上端面也大致处在同一水平面上。
第一凹部158的环形壁157的上端面在轴向方向上距隔板116的与第一凹部158的环形壁157的上端面相面对的下表面的距离设计为使得当定涡旋部件150处于卸载状态时定涡旋部件150与隔板116不接触。
第二凹部152的环形壁159的上端面在轴向方向上距隔板116的与第二凹部152的环形壁159的上端面相面对的下表面的距离设计为使得当定涡旋部件150处于卸载状态时定涡旋部件150与隔板116不接触。
通过这种布置，可以使得当定涡旋部件150处于卸载状态时定涡旋部件150不与隔板116发生碰撞或干涉，从而保护涡旋压缩机的部件不受损坏。
另外，第一密封构件S110的第一延伸部S111和第二延伸部S112一体形成并且第一密封构件S110具有大致L形的横截面，第一延伸部S111和第二延伸部S112之间可以形成大于90°但小于180°的角度。隔板116的第一凸台1161的径向外周面与定涡旋部件150的第一凹部158的环形壁157的径向内周面之间的径向距离小于或等于第一密封构件S110的厚度，如在图4中示意性示出的。
另外，第二密封构件S130的第一延伸部S131和第二延伸部S132一体形成并且第二密封构件S130具有大致L形的横截面，第一延伸部S131和第二延伸部S132之间可以形成大于90°但小于180°的角度。隔板116的第二凸台1261的径向外周面与定涡旋部件150的第二凹部258的环形壁159的径向内周面之间的径向距离小于或等于第二密封构件S130的厚度。
此外，第一弹性构件S120可以为螺旋弹簧，螺旋弹簧S120向第一密封构件S110提供轴向压紧载荷。第二弹性构件S140也可以为螺旋弹簧，螺旋弹簧S140向第二密封构件S130提供轴向压紧载荷。但是第一弹性构件S120和第二弹性构件S140并不限于螺旋弹簧，只要其能够将第一密封构件S110或第二密封构件S130保持压靠在第一凸台1161或第二凸台1261上即可。
现在参照图7和图8描述本发明的第二实施方式的涡旋压缩机的密封结构S200。图7是本发明的第二实施方式的涡旋压缩机的密封结构的局部剖视图，图8是图7中的密封结构的局部放大剖视图。
第二实施方式与第一实施方式的不同之处在于隔板的凸台构型以及定涡旋部件的凹部的构型，因而在第二实施方式中，将着重描述这些不同之处，而省略对与第一实施方式中部件相同的这些部件的描述。
在第二实施方式的涡旋压缩机的密封结构S200中，隔板216的第一 凸台2161的径向外周面与定涡旋部件的第一凹部258的径向内周面、例如与第一凹部258的环形壁257的径向内周面大致平行，如图7所示。
优选地，第一凸台2161的径向外周面沿轴向方向向下渐缩，并且第一凸台2161的径向外周面相对于第一凸台2161的下端面所处的平面形成第一角度α，第一角度α等于或小于90°，如图8所示。当第一角度α等于90°时，第一凸台2161和第一凹部258变成第一实施方式中的第一凸台1161和第一凹部158。
隔板216的第一凸台2161的径向外周面与定涡旋部件的第一凹部258的径向内周面、例如与第一凹部258的环形壁257的径向内周面之间的径向距离小于或等于第一密封构件S110的厚度。
类似地，涡旋压缩机的密封结构S200的第二凸台2161的径向外周面与定涡旋部件的第二凹部252的径向内周面、例如与第二凹部252的环形壁259的径向内周面大致平行，如图7所示。
优选地，第二凸台2162的径向外周面沿轴向方向向下渐缩，并且第二凸台2162的径向外周面相对于第二凸台2162的下端面所处的平面形成第二角度，第二角度等于或小于90°，如图7所示。当第二角度等于90°时，第二凸台2162和第二凹部252变成第一实施方式中的第二凸台1162和第二凹部152。
隔板216的第二凸台2162的径向外周面与定涡旋部件的第二凹部252的径向内周面、例如与第一凹部252的环形壁259的径向内周面之间的径向距离小于或等于第二密封构件S130的厚度。
通过本实施方式的涡旋压缩机的密封结构的这种布置，使得需要由密封构件进行密封的间隙由现有技术的轴向间隙转换为径向间隙，而这种径向间隙的设定不再受到在提供轴向柔性时定涡旋部件轴向向上移动的距离POP的影响和限制。这样，可以将密封构件的厚度设定为尽可能薄从而提供更佳的密封效果，另外，这种密封结构还可以设置在具有距离POP较大的涡旋压缩机中，从而确保距离POP较大的涡旋压缩机可以获得更佳的密封效果。
另外，在具有本实施方式中的这种密封结构的涡旋压缩机的制造和组装过程中，影响和限制这种径向间隙的尺寸环(公差环)相对较少， 这有助于进一步地降低密封构件的厚度，从而更好地提升密封性能。此外，这也可以在保证密封性能的同时适当地降低涡旋压缩机的制造精度和组装精度，从而可以降低整个涡旋压缩机的制造成本并且降低装配难度。此外，在具有这种密封结构的涡旋压缩机中，密封构件在压缩机装配的过程中不易弹出，从而能够有效地防止密封构件在装配过程中弹出。
尽管上文参照图1-8描述了本发明的多种实施方式，但是本领域技术人员应该理解，可以对本发明的一些方面做出进一步的变型和/或改进。
例如，在所述隔板的下表面上还设置有第二凸台，并且，所述涡旋压缩机还包括：第二密封构件，所述第二密封构件的第一延伸部构造成抵靠所述隔板的所述第二凸台的下端面并且所述第二密封构件的第二延伸部构造成抵靠所述定涡旋部件的第二凹部的环形壁以实现密封，从而将所述第二压力区域与所述壳体内的第三压力区域隔开，其中所述第三压力区域中的压力不同于所述第一压力区域和所述第二压力区域中的压力；以及第二弹性构件，所述第二弹性构件设置在所述第二凹部中，以将所述第二密封构件保持压靠在所述第二凸台上，其中，当所述定涡旋部件处于所述非卸载状态时，所述第二凸台保持压靠所述第二密封构件使得所述第二密封构件不会被所述第二压力区域和所述第三压力区域中压力较大的一个压力区域中的压力挤出或弹出，当所述定涡旋部件处于所述卸载状态时，所述第二凸台保持压靠所述第二密封构件并且所述第二凸台的所述下端面至少处在所述第二凹部中。
例如，所述第一凸台和所述第二凸台以一者位于另一者的径向内侧的方式布置，或者，所述第一密封构件和所述第二密封构件以一者位于另一者的径向内侧的方式布置。
例如，当所述定涡旋部件处于所述非卸载状态时，所述第一凸台的所述下端面处在所述第一凹部中或者与所述第一凹部的所述环形壁的上端面大致齐平。
例如，当所述定涡旋部件处于所述非卸载状态时，所述第一凸台的所述下端面在轴向方向上比所述第一凹部的所述环形壁的上端面至多高所述第一密封构件的厚度的大致一半。
例如，所述第二凸台的所述下端面和所述第一凸台的所述下端面大致处在同一水平面上并且/或者所述第二凹部的所述环形壁的上端面和所述 第一凹部的所述环形壁的上端面大致处在同一水平面上。
例如，所述第一凸台的径向外周面与所述第一凹部的所述环形壁的径向内周面大致平行。
例如，所述第一凸台的所述径向外周面沿轴向方向向下渐缩，并且所述第一凸台的所述径向外周面相对于所述第一凸台的所述下端面所处的平面形成第一角度，所述第一角度等于或小于90°。
例如，所述第一凸台的径向外周面与所述第一凹部的径向内周面之间的径向距离小于或等于所述第一密封构件的厚度。
例如，所述第二凸台的径向外周面大致平行于所述第一凸台的径向外周面，并且，所述第二凹部的所述环形壁的径向内周面大致平行于所述第一凹部的所述环形壁的径向内周面。
例如，所述第二凸台的径向外周面与所述第二凹部的径向内周面之间的径向距离小于或等于所述第二密封构件的厚度。
例如，所述第一凹部的所述环形壁的上端面在轴向方向上距所述隔板的与所述第一凹部的所述环形壁的所述上端面相面对的下表面的距离设计为使得当所述定涡旋部件处于所述卸载状态时所述定涡旋部件与所述隔板不接触。
例如，所述第二凹部的所述环形壁的上端面在轴向方向上距所述隔板的与所述第二凹部的所述环形壁的所述上端面相面对的下表面的距离设计为使得当所述定涡旋部件处于所述卸载状态时所述定涡旋部件与所述隔板不接触。
例如，所述第一密封构件的所述第一延伸部和所述第二延伸部一体形成并且所述第一密封构件具有大致L形的横截面并且/或者所述第二密封构件的所述第一延伸部和所述第二延伸部一体形成并且所述第二密封构件具有大致L形的横截面。
例如，所述第一压力区域对应于与进气压力连通的低压侧区域并且所述第二压力区域对应于与所述动涡旋部件和所述定涡旋部件之间形成的一系列压缩腔中的一个压缩腔连通的中压侧区域，或者，所述第一压力区域对应于与排气压力连通的高压侧区域并且所述第二压力区域对应于与 所述动涡旋部件和所述定涡旋部件之间形成的一系列压缩腔中的一个压缩腔连通的中压侧区域。
尽管在此已详细描述本发明的各种实施方式，但是应该理解本发明并不局限于这里详细描述和示出的具体实施方式，在不偏离本发明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发明的范围内。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 (15)

  1. 一种涡旋压缩机(100)，包括：
    壳体(110)；
    设置在所述壳体(110)内的压缩机构(150、160)，所述压缩机构(150、160)适于压缩工作流体并且包括定涡旋部件(150)和动涡旋部件(160)；
    隔板(116；216)，所述隔板(116；216)设置在所述壳体(110)内并且邻近所述定涡旋部件(150)，在所述隔板(116；216)的下表面上设置有第一凸台(1161；2161)；
    第一密封构件(S110)，所述第一密封构件(S110)的第一延伸部(S111)构造成抵靠所述隔板(116；216)的所述第一凸台(1161；2161)的下端面并且所述第一密封构件(S110)的第二延伸部(S112)构造成抵靠所述定涡旋部件(150)的第一凹部(158；258)的环形壁(157；257)以实现密封，从而将所述壳体(110)内的具有不同压力的第一压力区域与第二压力区域隔开；以及
    第一弹性构件(S120)，所述第一弹性构件(S120)设置在所述第一凹部(158；258)中，以将所述第一密封构件(S110)保持压靠在所述第一凸台(1161；2161)上，
    其中，所述定涡旋部件(150)能够在非卸载状态与卸载状态之间转换，当所述定涡旋部件(150)处于所述非卸载状态时，所述第一凸台(1161；2161)保持压靠所述第一密封构件(S110)使得所述第一密封构件(S110)不会被所述第一压力区域和所述第二压力区域中压力较大的一个压力区域中的压力挤出或弹出，当所述定涡旋部件(150)处于所述卸载状态时，所述第一凸台(1161；2161)保持压靠所述第一密封构件(S110)并且所述第一凸台(1161；2161)的所述下端面至少处在所述第一凹部(158；258)中。
  2. 根据权利要求1所述的涡旋压缩机(100)，其中，在所述隔板(116；216)的下表面上还设置有第二凸台(1162；2162)，并且，所述涡旋压缩机(100)还包括：
    第二密封构件(S130)，所述第二密封构件(S130)的第一延伸部 (S131)构造成抵靠所述隔板(116；216)的所述第二凸台(1162；2162)的下端面并且所述第二密封构件(S130)的第二延伸部(S132)构造成抵靠所述定涡旋部件(150)的第二凹部(152；252)的环形壁(159；259)以实现密封，从而将所述第二压力区域与所述壳体(110)内的第三压力区域隔开，其中所述第三压力区域中的压力不同于所述第一压力区域和所述第二压力区域中的压力；以及
    第二弹性构件(S140)，所述第二弹性构件(S140)设置在所述第二凹部(152；252)中，以将所述第二密封构件(S130)保持压靠在所述第二凸台(1162；2162)上，
    其中，当所述定涡旋部件(150)处于所述非卸载状态时，所述第二凸台(1162；2162)保持压靠所述第二密封构件(S130)使得所述第二密封构件(S130)不会被所述第二压力区域和所述第三压力区域中压力较大的一个压力区域中的压力挤出或弹出，当所述定涡旋部件(150)处于所述卸载状态时，所述第二凸台(1162；2162)保持压靠所述第二密封构件(S130)并且所述第二凸台(1162；2162)的所述下端面至少处在所述第二凹部(152；252)中。
  3. 根据权利要求2所述的涡旋压缩机(100)，其中，所述第一凸台(1161；2161)和所述第二凸台(1162；2162)以一者位于另一者的径向内侧的方式布置，或者，所述第一密封构件(S110)和所述第二密封构件(S130)以一者位于另一者的径向内侧的方式布置。
  4. 根据权利要求1所述的涡旋压缩机(100)，其中，当所述定涡旋部件(150)处于所述非卸载状态时，所述第一凸台(1161；2161)的所述下端面处在所述第一凹部(158；258)中或者与所述第一凹部(158；258)的所述环形壁(157；257)的上端面大致齐平。
  5. 根据权利要求1所述的涡旋压缩机(100)，其中，当所述定涡旋部件(150)处于所述非卸载状态时，所述第一凸台(1161；2161)的所述下端面在轴向方向上比所述第一凹部(158；258)的所述环形壁(157；257)的上端面至多高所述第一密封构件(S110)的厚度的大致一半。
  6. 根据权利要求2所述的涡旋压缩机(100)，其中，所述第二凸台(1162；2162)的所述下端面和所述第一凸台(1161；2161)的所述下端面大致处在同一水平面上并且/或者所述第二凹部(152；252)的所述环形壁(159；259)的上端面和所述第一凹部(158；258)的所述环形壁(157；257)的上端面大致处在同一水平面上。
  7. 根据权利要求1所述的涡旋压缩机(100)，其中，所述第一凸台(1161；2161)的径向外周面与所述第一凹部(158；258)的所述环形壁(157；257)的径向内周面大致平行。
  8. 根据权利要求7所述的涡旋压缩机(100)，其中，所述第一凸台(1161；2161)的所述径向外周面沿轴向方向向下渐缩，并且所述第一凸台(1161；2161)的所述径向外周面相对于所述第一凸台(1161；2161)的所述下端面所处的平面形成第一角度(α)，所述第一角度(α)等于或小于90°。
  9. 根据权利要求1至8中的任一项所述的涡旋压缩机(100)，其中，所述第一凸台(1161；2161)的径向外周面与所述第一凹部(158；258)的径向内周面之间的径向距离小于或等于所述第一密封构件(S110)的厚度。
  10. 根据权利要求2至8中的任一项所述的涡旋压缩机(100)，其中，所述第二凸台(1162；2162)的径向外周面大致平行于所述第一凸台(1161；2161)的径向外周面，并且，所述第二凹部(152；252)的所述环形壁(159；259)的径向内周面大致平行于所述第一凹部(158；258)的所述环形壁(157；257)的径向内周面。
  11. 根据权利要求2至8中的任一项所述的涡旋压缩机(100)，其中，所述第二凸台(1162；2162)的径向外周面与所述第二凹部(152；252)的径向内周面之间的径向距离小于或等于所述第二密封构件(S130)的厚度。
  12. 根据权利要求1至8中的任一项所述的涡旋压缩机(100)，其中，所述第一凹部(158；258)的所述环形壁(157；257)的上端面在轴向方向上距所述隔板(116；216)的与所述第一凹部(158；258)的所述环形壁(157；257)的所述上端面相面对的下表面的距离设计为使得当所述定涡旋部件(150)处于所述卸载状态时所述定涡旋部件(150)与所述隔板(116；216)不接触。
  13. 根据权利要求2至8中的任一项所述的涡旋压缩机(100)，其中，所述第二凹部(152；252)的所述环形壁(159；259)的上端面在轴向方向上距所述隔板(116；216)的与所述第二凹部(152；252)的所述环形壁(159；259)的所述上端面相面对的下表面的距离设计为使得当所述定涡旋部件(150)处于所述卸载状态时所述定涡旋部件(150)与所述隔板(116；216)不接触。
  14. 根据权利要求2至8中的任一项所述的涡旋压缩机(100)，其中，所述第一密封构件(S110)的所述第一延伸部(S111)和所述第二延伸部(S112)一体形成并且所述第一密封构件(S110)具有大致L形的横截面并且/或者所述第二密封构件(S130)的所述第一延伸部(S131)和所述第二延伸部(S132)一体形成并且所述第二密封构件(S130)具有大致L形的横截面。
  15. 根据权利要求1至8中的任一项所述的涡旋压缩机(100)，其中，所述第一压力区域对应于与进气压力连通的低压侧区域并且所述第二压力区域对应于与所述动涡旋部件(140)和所述定涡旋部件(150)之间形成的一系列压缩腔中的一个压缩腔连通的中压侧区域，或者，所述第一压力区域对应于与排气压力连通的高压侧区域并且所述第二压力区域对应于与所述动涡旋部件(140)和所述定涡旋部件(150)之间形成的一系列压缩腔中的一个压缩腔连通的中压侧区域。
PCT/CN2016/073067 2015-02-03 2016-02-01 涡旋压缩机 WO2016124120A1 (zh)

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