WO2013152705A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

Info

Publication number
WO2013152705A1
WO2013152705A1 PCT/CN2013/073917 CN2013073917W WO2013152705A1 WO 2013152705 A1 WO2013152705 A1 WO 2013152705A1 CN 2013073917 W CN2013073917 W CN 2013073917W WO 2013152705 A1 WO2013152705 A1 WO 2013152705A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
movable scroll
counterweight
scroll compressor
compressor according
Prior art date
Application number
PCT/CN2013/073917
Other languages
English (en)
Chinese (zh)
Inventor
苏晓耕
过炜华
孙庆丰
胡溱
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 CN2013200670540U external-priority patent/CN203146326U/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 IN2193MUN2014 priority Critical patent/IN2014MN02193A/en
Priority to US14/394,040 priority patent/US9879673B2/en
Publication of WO2013152705A1 publication Critical patent/WO2013152705A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/605—Balancing
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight

Definitions

  • the present invention relates to a scroll compressor. Background technique
  • the conventional scroll compressor 100 generally includes a housing 110, a top cover 112 disposed at the end of the housing 110, a bottom cover 114 disposed at the other end of the housing 110, and a cover disposed at the top cover. Between 112 and the housing 110 is partitioned into a partition 116 of the high pressure side and the low pressure side. A high pressure side is formed between the partition 116 and the top cover 112, and a low pressure side is formed between the partition 116, the casing 110 and the bottom cover 114. An intake joint 118 for sucking a fluid is provided on the low pressure side, and an exhaust joint 119 for discharging the compressed fluid is provided on the high pressure side.
  • 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 a compression mechanism comprised of the fixed scroll 150 and the movable scroll 160.
  • the movable scroll 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate.
  • the fixed scroll 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate.
  • 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 150 and the spiral blade 166 of the movable scroll 160. among them,
  • the radially outermost compression chamber C1 is at the suction pressure
  • the radially innermost compression chamber C3 is at the discharge 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.
  • One side of the movable scroll 160 is supported by an upper portion of the main bearing housing 140 (which constitutes a thrust member), and one end of the drive shaft 130 is supported by a main bearing 144 provided in the main bearing housing 140.
  • 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 160.
  • the translational rotation described above is achieved by a cross slip ring 190 disposed between the fixed scroll 150 and the movable scroll 160.
  • the fluid compressed by the fixed scroll 150 and the movable scroll 160 is discharged to the high pressure side through the exhaust port 152.
  • a check valve or exhaust valve 170 is provided at the exhaust port 152.
  • the fixed scroll 150 and the movable scroll 160 must be effectively sealed.
  • an axial seal is required between the tip end of the helical blade 156 of the fixed scroll 150 and the end plate 164 of the movable scroll 160 and between the tip end of the helical blade 166 of the movable scroll 160 and the end plate 154 of the fixed scroll 150.
  • a back pressure chamber 158 is provided on the side of the end plate 154 of the fixed scroll 150 opposite to the spiral blade 156.
  • a seal assembly 180 is disposed in the back pressure chamber 158, and the axial displacement of the seal assembly 180 is limited by the diaphragm 116.
  • the back pressure chamber 158 is in fluid communication with the intermediate pressure chamber C2 through an axially extending through hole (not shown) formed in the end plate 154 to form a force that urges the fixed scroll 150 toward the movable scroll 160. Since one side of the movable scroll 160 is supported by the upper portion of the main bearing housing 140, the constant scroll 150 and the movable scroll 160 can be effectively pressed together by the pressure in the back pressure chamber 158.
  • a radial seal is also required between the side surface of the spiral blade 156 of the fixed scroll 150 and the side surface of the spiral blade 166 of the movable scroll 160.
  • This radial seal between the two This is often achieved by the centrifugal force of the orbiting scroll 160 during operation and the driving force provided by the drive shaft 130.
  • the movable scroll 160 is rotated relative to the fixed scroll 150 by the driving of the motor 120 (ie, the central axis of the movable scroll 160 is rotated about the central axis of the fixed scroll 150, but The vortex 160 itself does not rotate about its central axis, so that the orbiting scroll 160 will generate centrifugal force.
  • the eccentric crank pin 132 of the drive shaft 130 also generates a driving force component that contributes to the radial seal of the fixed scroll and the movable scroll during the rotation.
  • the helical vanes 166 of the movable scroll 160 will abut against the helical vanes 156 of the fixed scroll 150 by means of the above-described centrifugal and driving force components, thereby achieving a radial seal therebetween.
  • Figure 2 shows a schematic view of the radial sealing force between the fixed scroll 150 and the movable scroll 160.
  • the total radial sealing force between the fixed scroll 150 and the movable scroll 160 can be expressed by the following equation:
  • F flank F IOS + F s Sin0 eff - F IO * Sin 0 - F rg Formula ( 1 ) where F flmk is the total radial sealing force between the fixed scroll 150 and the movable scroll 160;
  • F ROS is the centrifugal force of the movable scroll 160; it is the driving force component provided by the eccentric crank pin 132, where F s is the total driving force provided by the eccentric crank pin 132, which is the effective driving angle of the eccentric crank pin 132; is the cross slip ring 190
  • the centrifugal force component provided where. Is the total centrifugal force provided by the cross slip ring 190, ⁇ is the vortex 160 corresponding to the orientation angle of the fixed vortex 150; is the radial gas force provided by the fluid in the compression chamber.
  • ⁇ and ⁇ ⁇ ⁇ is an item related to the rotational speed of the drive shaft 130
  • / ⁇ # is an item irrelevant to the rotational speed of the drive shaft 130. Therefore, the radial sealing force F flmk is related to the rotational speed of the drive shaft 130. That is, the larger the rotational speed of the drive shaft 130, the larger the radial seal force F flank , and the smaller the rotational speed of the drive shaft 130, the smaller the radial seal force.
  • the radial sealing force F flank between the fixed scroll 150 and the movable scroll 160 may be insufficient to cause a decrease in compressor efficiency, while the scroll compressor 100 is in a high speed condition.
  • the radial sealing force between the fixed scroll 150 and the movable scroll 160 may be too large to cause excessive wear of the scroll member.
  • One object of one or more embodiments of the present invention is to provide a scroll compressor capable of ensuring a radial seal both under low speed conditions and high speed conditions.
  • Another object of one or more embodiments of the present invention is to provide a scroll compressor having a relatively simple structure while ensuring a radial seal.
  • a scroll compressor comprising: a fixed scroll including a fixed scroll end plate and a formation a fixed scroll blade on one side of the scroll end plate; an active scroll, the movable scroll includes an orbiting scroll end plate, an orbiting scroll blade formed on one side of the movable scroll end plate, and formed in the a hub portion on the other side of the scroll end plate; a drive shaft, the drive shaft includes an eccentric crank pin, and the eccentric crank pin is fitted in a hub portion of the movable scroll to drive the movable scroll;
  • the scroll compressor further includes an orbiting scroll counterweight that is configured to be rotatable with the drive shaft and a centrifugal force of the orbiting scroll counterweight due to rotation acts on the orbiting scroll On the hub.
  • the direction of the centrifugal force of the movable scroll counterweight is substantially opposite to the direction of the centrifugal force of the orbiting scroll.
  • the centrifugal force of the orbiting scroll counterweight is set to be substantially equal to the centrifugal force of the orbiting scroll.
  • the movable scroll weight comprises a cylindrical portion, the cylindrical portion is disposed to surround a hub of the movable scroll, and at least a portion of the cylindrical portion contacts an outer side of the hub .
  • a bearing is provided in the cylindrical portion of the movable scroll counterweight, and an inner side of the bearing contacts an outer side of the hub.
  • the bearing is a rolling bearing or a sliding bearing.
  • an outer peripheral surface of the drive shaft is provided with a driving portion for driving the movable scroll counterweight, the movable scroll counterweight includes a bottom wall and is disposed on the bottom wall a driving hole that the driving portion cooperates with.
  • the shape of the driving portion substantially corresponds to the shape of the driving hole.
  • the drive portion has a non-circular cross section.
  • the maximum dimension of the driving portion in the radial direction is smaller than or equal to the maximum dimension of the driving hole in the radial direction.
  • the driving portion and the driving hole are configured to allow the movable scroll counterweight to slide in the radial direction on the driving portion.
  • the driving portion includes two step portions each including a bottom surface and a side surface, and side surfaces of the two step portions are parallel to each other.
  • the drive hole has two side walls that are engageable with the sides of the two step portions.
  • the two side walls of the drive hole are parallel to each other.
  • each step portion is substantially parallel to the direction of the centrifugal force of the orbiting scroll.
  • the distance between the sides of the two step portions is substantially equal to the distance between the two side walls of the drive hole of the movable scroll counterweight.
  • the movable scroll counterweight is supported in the axial direction by a bottom surface of at least one of the stepped portions of the drive shaft.
  • an eccentric crank pin of the drive shaft is fitted in a hub of the movable scroll via an unloading bushing, the eccentric crank pin including a flat portion extending parallel to an axis of rotation of the drive shaft,
  • the unloading bushing includes a flat portion corresponding to a planar portion of the eccentric crank pin.
  • a gap between the eccentric crank pin and the unloading bushing in a radial direction parallel to a plane portion of the eccentric crank pin is Cl, assuming the drive shaft and the movement
  • the gap between the drive holes of the vortex counterweight in the radial direction parallel to the side wall of the drive hole is C2, and the relationship between C1 and C2 is set to C2 ⁇ C1.
  • the center of gravity of the movable scroll counterweight and the center of gravity of the movable scroll are located on both sides of the rotation axis of the drive shaft.
  • the mass of the orbiting scroll is M1
  • the minimum translational radius of the orbiting scroll is D1
  • the mass of the orbiting scroll is assumed to be M2
  • the orbiting scroll The maximum radius of gyration of the weight centroid is D2
  • a matching hole is disposed on an outer circumferential surface of the driving shaft, a driving hole is formed in a bottom wall of the movable scroll counterweight, and the scroll compressor further includes a driving rod, the driving rod The first end of the driving rod is engaged in the matching hole of the driving shaft, and the second end of the driving rod is engaged in the driving hole of the movable scroll weight.
  • the scroll compressor further includes a snap spring that fixably fits the movable scroll counterweight to the hub of the movable scroll.
  • the drive hole is a long hole extending substantially in a radial direction of the movable scroll weight.
  • a gap between the eccentric crank pin and the unloading bushing in a radial direction parallel to a plane portion of the eccentric crank pin is Cl, assuming a radial length of the elongated hole
  • the relationship between C1 and C3 is set to C3 ⁇ C1.
  • the drive rod is substantially L-shaped.
  • the scroll compressor further includes a main bearing housing supporting the drive shaft and a thrust plate supporting an end plate of the movable scroll, the main bearing housing and the thrust plate being Separate components are secured together by a fixture.
  • a space is formed between the main bearing housing and the thrust plate to allow the orbiting scroll to rotate.
  • the scroll compressor further includes a main bearing seat supporting the drive shaft And a thrust plate supporting the end plate of the movable scroll, the main bearing seat and the thrust plate being formed integrally.
  • the movable scroll counterweight includes a cylindrical portion disposed around a hub of the movable scroll, and at least one oil supply groove is disposed on an inner circumference of the cylindrical portion.
  • the oil supply groove extends substantially in the axial direction of the scroll compressor.
  • the pair of oil supply grooves are arranged substantially symmetrically with respect to a center of rotation of the movable scroll counterweight.
  • the height of the portion of the cylindrical portion of the movable scroll counterweight in which the oil supply groove is provided is raised with respect to the height of the other portion in the cylindrical portion.
  • a portion of the cylindrical portion of the movable scroll counterweight provided with the oil supply groove is configured to be adjacent to a lower surface of the movable scroll end plate.
  • the movable scroll counterweight further includes a bottom wall, and the bottom wall is formed with a step portion protruding with respect to the bottom wall.
  • the oil supply groove extends in the axial direction to the step portion.
  • a height at which the step portion protrudes with respect to the bottom wall is configured such that a lubricant flowing upward through the oil supply groove and a downward flow through a drive hole formed in the bottom wall The lubricant reaches a predetermined ratio.
  • an orbiting scroll counterweight is provided, and the movable scroll is reconfigured to cause a centrifugal force that can be rotated with the drive shaft and the movable scroll counterweight is rotated.
  • the direction of the centrifugal force of the movable scroll counterweight may be set to be substantially opposite to the direction of the centrifugal force of the movable scroll. Therefore, the centrifugal force of the movable scroll can be balanced by the centrifugal force of the movable scroll counterweight.
  • the radial sealing force between the movable scroll and the fixed scroll will depend primarily on the driving force provided by the eccentric crank pin of the drive shaft.
  • the centrifugal force of the movable scroll counterweight may be set to be substantially equal to the centrifugal force of the movable scroll. Therefore, the centrifugal force of the vortex can be offset by the complete passive vortex counterweight. It is therefore ensured that the radial sealing force between the two scroll members remains substantially constant at various rotational speeds, so that the scroll compressor can operate stably under various operating conditions.
  • the movable scroll counterweight may include a cylindrical portion that is disposed to surround the hub of the movable scroll, and at least a portion of the cylindrical portion contacts The outer side of the hub.
  • a bearing may be provided in the cylindrical portion of the movable scroll weight, and the inner side of the bearing contacts the outer side of the hub.
  • the bearing may be a rolling bearing or a plain bearing.
  • a driving portion for driving the movable scroll counterweight is provided on an outer peripheral surface of the drive shaft, and the movable scroll counterweight includes a bottom wall and is at the bottom wall A drive hole that cooperates with the drive portion is disposed on the upper portion. Therefore, the drive shaft can easily rotate the movable scroll counterweight together.
  • the shape of the driving portion substantially corresponds to the shape of the driving hole, for example, the driving portion may have a non- ⁇ -shaped cross section.
  • the driving portion and the driving hole may be any configuration capable of cooperating with each other for power transmission.
  • the maximum dimension of the driving portion in the radial direction may be set to be equal to or smaller than the maximum dimension of the driving hole in the radial direction.
  • the drive portion and the drive bore are configured to allow the movable scroll counterweight to slide in the radial direction on the drive portion.
  • the driving portion includes two step portions each including a bottom surface and a side surface, and side surfaces of the two step portions are parallel to each other. Further, the drive hole has two side walls that are engageable with the sides of the two step portions.
  • the side surface of each step portion may be substantially parallel to the direction of the centrifugal force of the movable scroll.
  • the moving scroll counterweight will only produce along the path The centrifugal force in the direction does not generate a component of the force in the other direction, and the design of the movable scroll counterweight is further compressed.
  • the distance between the sides of the two step portions may be substantially equal to the distance between the two side walls of the drive hole of the movable scroll counterweight. Therefore, when the drive shaft starts to rotate or stops rotating, there is no collision between the drive shaft and the movable scroll counterweight, thereby avoiding noise between the two.
  • the movable scroll counterweight is supported in the axial direction by the bottom surface of at least one of the step portions of the drive shaft.
  • the movable scroll counterweight can be placed directly on the bottom surface of at least one of the step portions of the drive shaft, thereby eliminating the need to further provide other members for axially retaining the movable scroll counterweight, simplifying the structure of the weight mechanism.
  • an eccentric crank pin of a drive shaft may be fitted in a hub of the movable scroll via an unloading bushing.
  • Cl the gap between the eccentric crank pin and the unloading bushing in the radial direction parallel to the plane portion of the eccentric crank pin
  • Cl the gap between the drive shaft and the drive hole of the movable scroll counterweight
  • C2 the relationship between C1 and C2 is set to C2 ⁇ C1.
  • the center of gravity of the movable scroll counterweight and the center of gravity of the movable scroll may be located on both sides of the rotation axis of the drive shaft.
  • the mass of the orbiting scroll is assumed to be Ml
  • the minimum translational radius of gyration of the orbiting scroll is D1
  • the mass of the orbiting scroll counterweight is assumed to be M2
  • the maximum radius of gyration of the centroid of the orbiting scroll is D2
  • the outer peripheral surface of the drive shaft may be provided with a fitting hole, and a driving hole may be formed in the bottom wall of the movable scroll counterweight, and the scroll compressor may further
  • the drive rod includes a first end of the drive rod engaged in a mating hole of the drive shaft, and a second end of the drive rod is fitted in the drive hole of the movable scroll counterweight.
  • the drive hole may be an elongated hole extending substantially in the radial direction of the movable scroll weight.
  • the gap between the eccentric crank pin and the unloading bushing in the radial direction parallel to the plane portion of the eccentric crank pin is Cl, and assuming that the radial length of the long hole is C3, the relationship between C1 and C3 is set to C3 ⁇ C1.
  • a space allowing the rotation of the movable scroll counterweight may be formed between the main bearing housing and the thrust plate.
  • the main bearing housing and the thrust plate are integrally formed, and may be formed as separate members and then fixed together by fixing means. With these configurations, the flexibility of the design of the movable scroll counterweight can be increased.
  • the main bearing housing and the thrust plate are separate components, it is also possible to provide a larger area of the thrust surface for the orbiting scroll by a suitably designed thrust plate to increase the operational stability of the scroll compressor and Durability.
  • the inner circumference of the cylindrical portion of the movable scroll counterweight is provided with at least one oil supply groove through which the oil supply groove can be easily and The lubricant is stably supplied to the thrust surface between the movable scroll end plate and the thrust plate, thereby achieving better lubrication.
  • the height of the portion of the cylindrical portion in which the oil supply groove is provided may be increased with respect to the height of the other portion of the cylindrical portion or the portion of the cylindrical portion in which the oil supply groove is provided may be configured to be adjacent to the movable scroll
  • the lower surface of the end plate makes it easier to supply the lubricant to the thrust surface of the movable scroll.
  • a step portion may be formed on the bottom wall of the movable scroll counterweight, by which the lubricant flowing upward through the oil supply groove and the lubricant flowing downward through the driving hole formed in the bottom wall may be controlled
  • the ratio is such that a reasonable supply of lubricant to each of the parts requiring lubrication is achieved.
  • Figure 1 is a longitudinal sectional view of a conventional scroll compressor
  • Figure 2 is a schematic view of the radial sealing force between the orbiting scroll and the fixed scroll of Figure 1;
  • Figure 3 is a longitudinal sectional view showing a scroll compressor according to a first embodiment of the present invention
  • Figure 4 is an exploded perspective view of the relevant components around the movable scroll counterweight according to the first embodiment of the present invention
  • Figure 5 shows an assembled perspective view of the components shown in Figure 4;
  • Figure 6A is a perspective view of a drive shaft according to a first embodiment of the present invention
  • Figure 6B is a perspective view of another angle of the drive shaft
  • Figure 6C is an end view of the drive shaft
  • Figure 7A is a perspective view of an active scroll counterweight according to a first embodiment of the present invention
  • Figure 7B is a longitudinal cross-sectional view of the movable scroll counterweight
  • Figure 8A is a perspective view of a main bearing housing and a thrust plate according to a first embodiment of the present invention
  • Figure 8B is a partial cross-sectional perspective view of the main bearing housing and the thrust plate
  • Figure 9 is an enlarged longitudinal cross-sectional view of the movable scroll counterweight according to the first embodiment of the present invention.
  • Figure 10 is a plan sectional view taken along line AA of Figure 9;
  • Figure 81 is a partial enlarged view of Figure 10 showing the relationship between the drive shaft, the movable scroll counterweight and the unloading bushing. ;
  • Figure 82 is a schematic view showing the radial sealing force between the movable scroll and the fixed scroll according to the first embodiment of the present invention
  • Figure 13 is a schematic diagram showing the relationship between the mass of the movable scroll and the movable scroll counterweight and the radius of gyration;
  • Figure 14 is a partial longitudinal sectional view showing a scroll compressor according to a modification of the first embodiment of the present invention.
  • 15A and 15B are perspective views showing different directions of the movable scroll counterweight according to a modification of the first embodiment of the present invention.
  • FIG. 16 is a partial longitudinal sectional view showing a scroll compressor according to a second embodiment of the present invention
  • 17A and 17B are perspective views showing different directions of an orbiting scroll weight according to a second embodiment of the present invention
  • FIG. 18 is a perspective view showing a drive shaft according to a second embodiment of the present invention
  • Figure 19 is a perspective view showing a drive lever according to a second embodiment of the present invention.
  • FIG. 20 shows a perspective view of a circlip according to a second embodiment of the present invention.
  • FIGS. 21A and 21B are perspective views showing different directions of the movable scroll counterweight according to a modification of the second embodiment of the present invention.
  • Fig. 22 is a view showing the supply of the lubricant in the scroll compressor according to the first embodiment of the present invention. detailed description
  • the scroll compressor 10 generally includes a housing 110, a top cover 112 disposed at one end of the housing 110, a bottom cover 114 disposed at the other end of the housing 110, and a setting Between the top cover 112 and the housing 110 is partitioned into a partition 116 of the high pressure side and the low pressure side. A high pressure side is formed between the partition 116 and the top cover 112, and a low pressure side is formed between the partition 116, the casing 110 and the bottom cover 114. An intake joint 118 for sucking a fluid is provided on the low pressure side, and an exhaust joint 119 for discharging the compressed fluid is provided on the high pressure side.
  • a motor 120 composed of a stator 122 and a rotor 124 is disposed in the housing 110.
  • a drive shaft 30 is disposed in the rotor 124 to drive a compression mechanism comprised of the fixed scroll 150 and the movable scroll 160.
  • the movable scroll 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate.
  • the fixed scroll 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate.
  • 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 vane 156 of the fixed scroll 150 and the spiral vane 166 of the movable scroll 160.
  • the radially outermost compression chamber C1 is at the suction pressure
  • the radially innermost compression chamber C3 is 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.
  • a portion of the drive shaft 30 is supported by a main bearing 144 disposed in the main bearing housing 20.
  • One end of the drive shaft 30 is formed with an eccentric crank pin 32.
  • the eccentric crank pin 32 is fitted into the hub portion 162 of the movable scroll 160 via the unloading bushing 60 to drive the movable scroll 160.
  • the eccentric crank pin 32 includes a flat portion extending parallel to the rotational axis of the drive shaft 30.
  • the unloading bushing 60 includes a flat portion 62 corresponding to the flat portion 321 of the eccentric crank pin.
  • [99J main bearing housing 20 is provided with a thrust plate 50.
  • the thrust plate 50 can be fixed to the main bearing housing 20 by a fixing means (see Figs. 8A and 8B).
  • a space S is formed between the main bearing housing 20 and the thrust plate 50.
  • One side of the movable scroll 160 is supported by the thrust plate 50.
  • the translational rotation described above is achieved by a cross slip ring 190 disposed between the fixed scroll 150 and the movable scroll 160.
  • the fluid compressed by the fixed scroll 150 and the movable scroll 160 is discharged to the high pressure side through the exhaust port 152.
  • a one-way valve or exhaust valve 170 is provided at the exhaust port 152.
  • a back pressure chamber 158 is provided on the opposite side of the end plate 154 of the fixed scroll 150 from the spiral vane 156.
  • a seal assembly 180 is disposed in the back pressure chamber 158, and the axial displacement of the seal assembly 180 is limited by the diaphragm 116.
  • the back pressure chamber 158 is in fluid communication with the intermediate pressure chamber C2 through an axially extending through bore (not shown) formed in the end plate 154 to form a force that urges the fixed scroll 150 toward the movable scroll 160. Since one side of the movable scroll 160 is supported by the upper portion of the main bearing housing 140, the constant scroll 150 and the movable scroll 160 can be effectively pressed together by the pressure in the back pressure chamber 158. These compression scrolls 150 move upward when the pressure in each compression chamber exceeds a set value.
  • the fluid in the cavity will have a gap between the tip end of the spiral blade 156 of the predetermined scroll 150 and the end plate 164 of the movable scroll 160 and the tip end of the spiral blade 166 of the movable scroll 160 and the fixed scroll.
  • the gap between the end plates 154 of 150 leaks to the low pressure side to Unloading is achieved, providing axial flexibility to the scroll compressor.
  • the scroll compressor 10 is further provided with a movable scroll counterweight 40 while maintaining a suitable value in both the high speed operating condition and the low speed operating condition.
  • the movable scroll counterweight 40 is configured to be rotatable with the drive shaft 30 and the centrifugal force of the movable scroll counterweight 40 due to the rotation acts on the hub portion 162 of the movable scroll 160.
  • the direction of the centrifugal force of the orbiting scroll counterweight 40 may be set to be substantially opposite to the direction of the centrifugal force of the orbiting scroll 160. Therefore, the movable scroll counterweight can most effectively counteract the centrifugal force of the movable scroll 160.
  • the centrifugal force of the movable scroll counterweight 40 can be set to be substantially equal to the centrifugal force of the movable scroll 160. In this case, the centrifugal force of the movable scroll 160 can be completely offset by the passive vortex counterweight 40.
  • the centrifugal force of the movable scroll counterweight 40 can also be set to be different from the centrifugal force of the orbiting scroll 160.
  • the centrifugal force of the movable scroll 160 is at least partially offset by the centrifugal force of the passive scroll counterweight 40, thereby also reducing the radial sealing force between the scroll members at high speed conditions and low speed conditions. The difference is made to avoid poor sealing at low speeds and excessive wear at high speeds.
  • the movable scroll counterweight 40 may include a cylindrical portion 42, and the cylindrical portion 42 is disposed to surround the hub portion 162 of the movable scroll 160.
  • a bearing 46 is provided in the cylindrical portion 42 of the movable scroll counterweight 40, and the inner side of the bearing 46 contacts the outer side of the hub portion 162.
  • Bearing 46 can be a rolling or plain bearing or any other suitable bearing.
  • the bearing 46 facilitates the transfer of force between the orbiting scroll weight 40 and the hub 162 of the orbiting scroll 160 and helps to reduce wear between the two.
  • the bearing 46 can also be omitted, as shown in Figures 14 and 15A, 15B.
  • the movable scroll counterweight 40 may be disposed such that at least a portion of its cylindrical portion 42 contacts the outer side of the hub portion 162.
  • a drive portion 33 for rotating the movable scroll counterweight 40 may be provided on the outer peripheral surface of the drive shaft 30.
  • the movable scroll counterweight 40 may include a bottom wall 44 and a drive hole 48 that cooperates with the driving portion 33 may be disposed on the bottom wall 44.
  • the shape of the driving portion 33 may be set to substantially correspond to the shape of the driving hole 48.
  • the drive portion 33 may have any non-circular cross section to drive the movable scroll counterweight 40 without considering providing radial flexibility to the compressor.
  • the driving portion 33 and the driving hole 48 may be any configuration capable of performing power transmission in cooperation with each other.
  • the radial direction of the drive portion 33 The maximum size may be set to be equal to or smaller than the maximum dimension of the drive hole 48 in the radial direction.
  • the driving portion 33 and the driving hole 48 may be configured to allow the movable scroll counterweight 40 to slide in the radial direction on the driving portion 33.
  • the driving portion 33 may include two step portions 34 and 35, each of the step portions 34, 35 including a bottom surface 341, 351 and side surfaces 342, 352, respectively.
  • the side faces 342, 352 of the step portions 34, 35 are parallel to each other.
  • a drive hole 48 is formed in the bottom wall 44 of the movable scroll weight 40, and the drive hole 48 has two seats 342, 352 that can be engaged with the two step portions 34, 35 of the drive shaft 30.
  • the drive bore 48 also has two curved side walls 483 and 484 that are connected to the two side walls 481, 482, respectively.
  • the two side walls 481, 482 of the drive aperture 48 are parallel to each other.
  • the sides 342, 352 of each of the step portions 34, 35 may be configured to be substantially parallel to the direction of the centrifugal force of the orbiting scroll 160.
  • the distance between the sides 342, 352 of the two step portions 34, 35 can be set to be substantially equal to the distance between the two side walls 481, 482 of the drive bore 48 of the movable scroll counterweight 40.
  • the movable scroll counterweight 40 is supported in the axial direction by the bottom surfaces 341, 351 of at least one of the step portions 34, 35 of the drive shaft 30.
  • the gap between the eccentric crank pin 32 and the unloading bushing 60 in the radial direction parallel to the plane portion 321 of the eccentric crank pin 32 is Cl, assuming that the drive shaft 30 is moving
  • the gap between the drive holes 48 of the scroll weight 40 in the radial direction parallel to the side walls 481, 482 of the drive hole 48 is C2, and the relationship between C1 and C2 can be set to C2 ⁇ C1.
  • the gap C1 is the total gap in the radial direction between the eccentric crank pin 32 and the unloading bushing 60
  • the gap C2 is the drive hole 48 of the drive shaft 30 and the movable scroll counterweight 40.
  • the movable scroll counterweight 40 when the drive shaft 30 drives the movable scroll 160 to rotate, the movable scroll counterweight 40 will synchronously rotate the follower scroll 160 via the cooperation between the drive hole 48 and the step portions 34, 35.
  • the centrifugal force generated by the movable scroll counterweight 40 is transmitted through the cylindrical portion 42 and the bearing 46 to the hub portion 162 of the movable scroll 160. Since the orbiting scroll weight 40 is assembled such that the direction of its centrifugal force is substantially opposite to the direction of the centrifugal force of the orbiting scroll 160, the centrifugal force of the orbiting scroll counterweight 40 can cancel at least a portion of the centrifugal force of the orbiting scroll 160.
  • the centrifugal force of the movable scroll counterweight 40 is set to be substantially the same as the centrifugal force of the orbiting scroll 160, the centrifugal force of the movable scroll 160 is completely canceled. In this case, regardless of whether the rotational speed of the drive shaft 30 is high or low, the radial sealing force between the movable scroll and the fixed scroll is independent of the centrifugal force of the movable scroll 160.
  • F ros is the centrifugal force of the movable scroll 160; it is the driving force component provided by the eccentric crank pin 32, wherein the total driving force provided by the eccentric crank pin 32 is the effective driving angle of the eccentric crank pin 32; it is provided by the cross slip ring 190 Centrifugal force component, where. Is the total centrifugal force provided by the cross slip ring 190, ⁇ is the vortex 160 corresponding to the orientation angle of the fixed scroll 150; is the gas force provided by the fluid in the compression chamber,
  • F m is the centrifugal force of the movable scroll counterweight 40.
  • Equation 3 only . *>3 ⁇ 4 ⁇ is an item related to the rotational speed of the drive shaft 130. However, since the weight of the cross slip ring 190 is small, this item is almost negligible. ⁇ is an item independent of the rotational speed of the drive shaft 130 and can be considered as a constant. It is also an item that is independent of the rotational speed of the drive shaft 130, and can be considered as a constant when the effective drive angle is fixed. However, the size of the item can be changed by changing the ⁇ driving angle ⁇ of the eccentric crank pin 32.
  • the radial sealing force is a constant irrespective of the rotational speed of the drive shaft 130.
  • the radial sealing force / is constant.
  • the magnitude of F s Sin0 eff can be changed by changing the effective driving angle of the eccentric crank pin 32, the required radial sealing force / ⁇ can be adjusted by adjusting the effective driving angle. founded 3 ⁇ 4 .
  • a suitable radial sealing force can be achieved. The compressor efficiency is reduced due to insufficient radial sealing force. Also, excessive wear of the scroll member caused by excessive radial sealing force is avoided.
  • the gap C2 in the radial direction between the drive shaft 30 and the drive hole 48 of the movable scroll counterweight 40 is set to be equal to or larger than between the eccentric crank pin 32 and the unloading bushing 60.
  • the maximum distance that the orbiting scroll 160 can be radially offset is Cl, at which time foreign matter is allowed to pass between the spiral vanes 156 and the spiral vanes 166 that are radially separated from each other.
  • the orbiting scroll 160 causes the movable scroll counterweight 40 to be radially displaced when radially displaced.
  • the gap C2 between the drive hole 48 of the movable scroll counterweight 40 and the drive shaft 30 is greater than or equal to the gap C1 described above, the radial offset of the movable scroll counterweight 40 is not blocked by the drive shaft 30.
  • both the movable scroll 160 and the movable scroll counterweight 40 can perform a radial offset with a maximum distance of C1.
  • the scroll compressor is provided with a constant radial sealing force while still providing radial flexibility to the scroll compressor.
  • the unloading bushing 60 can be omitted without the need to provide a clearance C2 without the need to provide radial flexibility to the scroll compressor.
  • the fit between the drive shaft and the movable scroll counterweight may be any structure that enables the drive shaft to drive the movable scroll counterweight to rotate, and is not limited to the configurations shown in Figs.
  • a D-shaped section may be provided on the drive shaft 30, and accordingly, the movable scroll counterweight 40 may have a matching D-shaped aperture.
  • a key may be provided on the drive shaft 30, a keyway is provided in the drive hole 48, and the radial dimension of the drive hole 48 is set to be larger than the radial dimension of the drive shaft 30 so that the key of the drive shaft 30 can be fitted to the drive hole
  • the movable scroll counterweight is driven in the keyway of 48 while allowing the movable scroll counterweight to slide radially relative to the drive shaft along the key.
  • the movable scroll counterweight 40 may include a hub portion extending downward to surround the drive shaft 30. The inner diameter of the hub portion may be larger than the outer diameter of the drive shaft, and holes may be respectively disposed on the hub portion and the drive shaft, and a pin may be disposed.
  • the drive shaft can also drive the orbiting scroll counterweight rotation and allow the orbiting scroll counterweight to slide radially along the pin relative to the drive shaft.
  • the center of gravity M2 of the movable scroll counterweight 40 and the center of gravity M1 of the movable scroll 160 are located on both sides of the rotational axis O of the drive shaft 30.
  • the mass of the movable scroll 160 is M1
  • the minimum translational radius of gyration of the movable scroll 160 is D1
  • the mass of the movable scroll counterweight 40 is assumed to be M2
  • the maximum radius of gyration of the centroid of the movable scroll counterweight 40 is D2.
  • the mass of the movable scroll counterweight 40 and its radius of gyration can be easily set and it can be ensured that the movable scroll 160 can be in any case (including in the case where radial flexibility is performed) Securely engaged with the fixed scroll 150.
  • the present embodiment is different from the first embodiment in that the cooperation and the connection relationship between the movable scroll weight and the hub of the drive shaft and the movable scroll are different.
  • a fitting hole 36 may be provided on the outer peripheral surface of the drive shaft 30, and a drive hole 49 may be formed in the bottom wall of the movable scroll counterweight 40.
  • the movable scroll counterweight 40 and the drive shaft 30 can be coupled to each other by a drive lever 70.
  • the first end 72 of the drive rod 70 can fit in a mating bore 36 of the drive shaft 30, and the second end 74 of the drive rod 70 can fit within the drive bore 49 of the movable scroll counterweight 40.
  • the cylindrical portion 42 of the movable scroll counterweight 40 is disposed to surround the hub portion 162 of the movable scroll 160.
  • a snap spring 80 may be disposed outside the hub portion 162 of the movable scroll 160 to hold the movable scroll counterweight 40 in the axial direction.
  • the bearing 46 may be provided in the cylindrical portion 42, and the bearing 46 may be omitted as in the modification shown in Figs. 21A and 21B.
  • the drive lever 70 can be generally L-shaped. However, those skilled in the art will appreciate that the drive rod 70 can be any other shape suitable for driving the movable scroll counterweight.
  • the drive hole 49 may be an elongated hole extending substantially in the radial direction of the movable scroll weight 40.
  • the relationship between the mass of the movable scroll and the movable scroll counterweight and the radius of gyration can be set to satisfy the above formula 4.
  • the lubricant supply structure in the movable scroll counterweight 40 will be described below with further reference to Figs. 7A and 7B. More specifically, at least one oil supply groove 410 and 411 may be provided on the inner circumference of the cylindrical portion 42 of the movable scroll weight 40.
  • the oil supply grooves 410 and 411 may extend substantially in the axial direction of the scroll compressor. However, it will be understood by those skilled in the art that the oil supply grooves 410 and 411 may also extend in a manner inclined to correspond to the axial direction of the scroll compressor. In Figs.
  • the oil supply grooves 410 and 411 are provided in a pair, and the pair of oil supply grooves 410 and 411 can be arranged substantially symmetrically with respect to the center of rotation of the movable scroll weight 40, for example.
  • the oil supply groove 410 is shown as being disposed on the side of the cylindrical portion 42 near the thickened portion 49
  • the oil supply groove 411 is shown as being disposed in the cylindrical portion 42.
  • the opposite side of the thick portion 49 but those skilled in the art should understand that the number and position of the oil supply grooves can be arbitrarily set as needed.
  • the oil supply grooves 410 and 411 can be respectively They are disposed on both sides of the thickened portion 49.
  • the oil supply grooves 410 and 411 may extend in the axial direction to the bottom wall 44 of the movable scroll counterweight 40.
  • the drive shaft 30 includes a center hole 37 at a substantially central portion of the lower end and an eccentric hole 38 extending upward from the center hole 37 in the axial direction of the drive shaft 30 to the end surface of the eccentric crank pin 32.
  • the lubricant located at the bottom of the compressor housing is supplied into the center hole 37, for example, by a lubricant supply device such as a pump, and further moves upward along the eccentric hole 38 due to the centrifugal force generated by the rotation of the drive shaft 30 and finally from the eccentric crank pin.
  • the end of 32 is discharged.
  • the lubricant discharged from the eccentric crank pin 32 flows as indicated by arrows A and B. More specifically, a portion of the lubricant referred to by arrow A will move radially outward along the bottom wall 44 of the movable scroll counterweight 40 by centrifugal force until reaching the lower ends of the oil supply grooves 410 and 411. Then, the lubricant is pulled in the thrust surface along the oil supply groove 410, thereby lubricating it. Further, in this process, the lubricant also lubricates the bearing 46 provided inside the cylindrical portion 42. On the other hand, a part of the lubricant indicated by the arrow B will move downward by gravity and concentrate in the recess of the main bearing housing 20. The lubricant concentrated in the recess of the main bearing housing 20 will continue to flow downward to pass through the main bearing 144 and splash onto other moving parts due to the rotation of the drive shaft 30 to achieve lubrication.
  • the cylindrical portion of the movable scroll counterweight 40 42 The height of the portion where the oil supply grooves 410, 411 are provided may be raised with respect to the height of the other portions in the cylindrical portion 42.
  • a portion of the cylindrical portion 42 of the movable scroll counterweight 40 provided with the oil supply grooves 410, 411 is configured to be adjacent to the lower surface of the movable scroll end plate 164. In this way, the lubricant can reach the position closer to the movable scroll end plate 164 along the oil supply grooves 410, 411, thereby achieving a better lubrication effect.
  • the bottom wall 44 of the movable scroll counterweight 40 may also be formed with a step portion 412 protruding relative to the bottom wall 44.
  • the oil supply grooves 410, 411 may extend to the step portion 412 in the axial direction.
  • the step portion 412 is shown as a stepped portion extending in the circumferential direction in FIGS. 7A and 7B, it will be understood by those skilled in the art that the step portion 412 may be formed only at the lower end of the oil supply groove 410, 411. nearby.
  • the height at which the step portion 412 protrudes relative to the bottom wall 44 may be configured such that the lubricant flowing upward through the oil supply grooves 410, 411 (the lubricant indicated by the arrow A in Fig. 22) and the passage through the bottom wall 44 are formed.
  • the lubricant (the lubricant indicated by arrow B in Fig. 22) of the drive hole 48 flows downward to a predetermined ratio.
  • the bottom wall 44 of the movable scroll counterweight 40 may be omitted, such as shown in FIGS. 17A, 17B and FIGS. 21A and 21B, in which case the lubricant splashes as the drive shaft 30 rotates, Therefore, the oil supply grooves 410, 411 formed in the cylindrical portion 42 still contribute to the supply of lubricant and the vortex counterweight 40 to the thrust surface between the movable scroll end plate 164 and the thrust plate 50. Lubricant is supplied between the hub portions 162 of the movable scroll 160.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

Compresseur (10) à spirale, comprenant une spirale fixe (150), une spirale mobile (160) et un arbre d'entraînement (30); le compresseur (10) à spirale comprend en outre un contrepoids (40) de spirale mobile; le contrepoids (40) de spirale mobile est configuré pour tourner avec l'arbre d'entraînement (30); et la force centrifuge du contrepoids (40) de spirale mobile provoquée par la rotation agit sur le moyeu (162) de la spirale mobile (160). La structure ci-dessus peut efficacement réduire l'impact de la force centrifuge de la spirale mobile sur le joint radial d'un composant de spirale, obtenant ainsi la bonne force d'étanchéité radiale entre la spirale fixe et la spirale mobile à toute vitesse de rotation.
PCT/CN2013/073917 2012-04-11 2013-04-09 Compresseur à spirale WO2013152705A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
IN2193MUN2014 IN2014MN02193A (fr) 2012-04-11 2013-04-09
US14/394,040 US9879673B2 (en) 2012-04-11 2013-04-09 Scroll compressor

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
CN201220151455 2012-04-11
CN201210105213.1 2012-04-11
CN201210105213 2012-04-11
CN201220151455.X 2012-04-11
CN2013200670540U CN203146326U (zh) 2012-04-11 2013-02-05 涡旋压缩机
CN201320067054.0 2013-02-05
CN201310045737.0A CN103375402B (zh) 2012-04-11 2013-02-05 涡旋压缩机
CN201310045737.0 2013-02-05

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WO2013152705A1 true WO2013152705A1 (fr) 2013-10-17

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3116571A1 (fr) * 2020-11-25 2022-05-27 Danfoss Commercial Compressors Un contrepoids pour un compresseur à spirales

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4597724A (en) * 1983-03-31 1986-07-01 Sanden Corporation Scroll type fluid displacement apparatus with centrifugal force balanceweight
US5366359A (en) * 1993-08-20 1994-11-22 General Motors Corporation Scroll compressor orbital scroll drive and anti-rotation assembly
JPH0835493A (ja) * 1994-07-25 1996-02-06 Toyota Autom Loom Works Ltd スクロール型圧縮機
JP2002332976A (ja) * 2001-05-11 2002-11-22 Sanden Corp スクロール型流体機械
CN101297117A (zh) * 2005-10-26 2008-10-29 艾默生环境优化技术有限公司 涡旋压缩机
CN201206549Y (zh) * 2007-09-11 2009-03-11 艾默生环境优化技术有限公司 涡旋压缩机
CN101900113A (zh) * 2009-05-15 2010-12-01 艾默生环境优化技术有限公司 压缩机和油冷却系统

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4597724A (en) * 1983-03-31 1986-07-01 Sanden Corporation Scroll type fluid displacement apparatus with centrifugal force balanceweight
US5366359A (en) * 1993-08-20 1994-11-22 General Motors Corporation Scroll compressor orbital scroll drive and anti-rotation assembly
JPH0835493A (ja) * 1994-07-25 1996-02-06 Toyota Autom Loom Works Ltd スクロール型圧縮機
JP2002332976A (ja) * 2001-05-11 2002-11-22 Sanden Corp スクロール型流体機械
CN101297117A (zh) * 2005-10-26 2008-10-29 艾默生环境优化技术有限公司 涡旋压缩机
CN201206549Y (zh) * 2007-09-11 2009-03-11 艾默生环境优化技术有限公司 涡旋压缩机
CN101900113A (zh) * 2009-05-15 2010-12-01 艾默生环境优化技术有限公司 压缩机和油冷却系统

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3116571A1 (fr) * 2020-11-25 2022-05-27 Danfoss Commercial Compressors Un contrepoids pour un compresseur à spirales
WO2022112336A1 (fr) * 2020-11-25 2022-06-02 Danfoss Commercial Compressors Contrepoids pour compresseur à spirale

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