WO2012167610A1 - 一种带有绕动式推力轴承涡卷式容积位移装置 - Google Patents

一种带有绕动式推力轴承涡卷式容积位移装置 Download PDF

Info

Publication number
WO2012167610A1
WO2012167610A1 PCT/CN2012/000772 CN2012000772W WO2012167610A1 WO 2012167610 A1 WO2012167610 A1 WO 2012167610A1 CN 2012000772 W CN2012000772 W CN 2012000772W WO 2012167610 A1 WO2012167610 A1 WO 2012167610A1
Authority
WO
WIPO (PCT)
Prior art keywords
orbiting
scroll
bearing
thrust
thrust bearing
Prior art date
Application number
PCT/CN2012/000772
Other languages
English (en)
French (fr)
Inventor
倪诗茂
Original Assignee
思科涡旋科技(杭州)有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 思科涡旋科技(杭州)有限公司 filed Critical 思科涡旋科技(杭州)有限公司
Priority to US14/124,321 priority Critical patent/US20140140877A1/en
Publication of WO2012167610A1 publication Critical patent/WO2012167610A1/zh

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
    • 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
    • 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
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • 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
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/42—Pumps with cylinders or pistons

Definitions

  • the present invention relates to a scroll volume displacement device, and more particularly to a scroll volume displacement device for improving axial and radial scroll compliance structures.
  • scroll-type fluid displacement devices are used for compressors and expanders, and the scroll is an element that extends a cylindrical surface having a spiral profile on an end plate.
  • a fixed scroll usually one is fixed, called a fixed scroll.
  • the other scroll has a helical cylindrical surface conjugated to the helical cylindrical surface of the fixed scroll, and a circular translation, also called orbiting, with respect to the fixed scroll, is called an orbiting scroll.
  • the mutually conjugated spiral scroll faces of the two scrolls mesh with each other to form a line contact.
  • At least one sealed air chamber is formed between the pair of line contacts and the surface of the end plate.
  • FIG. 1 is a longitudinal cross-sectional view of an example of a scroll expander having a single scroll structure, see FIG. 1, an example of a scroll expander having a single scroll structure
  • the scroll device 10 includes a main housing 20, a base housing 70, a rotary drive shaft 40, a fixed scroll 50 and an orbiting scroll 60.
  • the orbiting scroll 60 has a second end plate 61.
  • the casing 70 is connected to the main casing 20, and the main casing 20 is provided with a fixed scroll 50 and an orbiting wrap 60.
  • Achieving a hermetic contact of the sealing element is to provide one or more, such as a sealing boss and a seal, on the orbiting scroll Sealing elements such as rings.
  • this method has two problems. First, when the sealing element is orbiting with the orbiting scroll, the orbiting scroll will be wound perpendicular to the main axis when orbiting under various forces and moments. The sway of the axis of the SI-S1, as shown by NN in Fig. 1, makes the sealing contact of the sealing boss 64 and the thrust bearing 71 easy to loosen. Second, frictional power loss and wear of the sealing member occur when sliding contact between the sealing member that makes the orbiting motion in the oil-free state and the thrust bearing. Summary of the invention
  • the present invention provides a scroll type volume displacement device having a mechanism capable of improving the reliability of a scroll to a compliant structure and improving the energy efficiency of the scroll device, and has a thrust bearing that performs an orbiting motion similar to that of the orbiting scroll Therefore, there is substantially no relative movement between the orbiting scroll and the thrust bearing, and a sealing contact is formed between the back surface of the orbiting scroll and the orbiting thrust bearing through a sealing member (for example, a sealing boss, an O-ring, a lip seal, etc.) Thereby forming a sealed pressure chamber.
  • a sealing member for example, a sealing boss, an O-ring, a lip seal, etc.
  • a scroll type displacement device with an orbiting thrust bearing comprising a main housing, a base housing, a fixed scroll and an orbiting scroll; wherein: further comprising an orbiting thrust bearing,
  • the orbiting thrust bearing is coupled to the bearing housing end plate of the orbiting scroll by a pin and a pin, the orbiting thrust bearing making an orbiting motion similar to the orbiting scroll.
  • the orbiting thrust bearing is in sliding engagement with the pin and the pin, and the orbiting scroll drives the orbiting thrust bearing to move by the pin and the pin.
  • the orbiting scroll has a second end plate, and the bypass thrust bearing forms a closed pressure chamber with the second end plate of the orbiting scroll, and the pressure of the pressure chamber Acting on the second end plate of the orbiting scroll such that the orbiting scroll makes a compliant movement relative to the fixed scroll.
  • a fixed thrust bearing is further included between the second end plate of the orbiting scroll and the base casing, and the fixed thrust bearing is connected with the orbiting thrust bearing, so that the orbiting thrust bearing The axial thrust received is absorbed by the fixed thrust bearing.
  • the fixed thrust bearing includes a fixed thrust ball bearing and a orbiting thrust ball bearing, the fixed thrust ball bearing is disposed on the base casing, and the orbiting thrust ball bearing acts on the fixed thrust ball bearing Above, at the same time, the orbiting thrust ball bearing performs a similar orbiting motion with respect to the fixed thrust ball bearing.
  • the axial thrust of the orbiting thrust bearing is received by the fixed thrust ball bearing and the orbiting thrust ball bearing.
  • the invention provides a scroll type volume displacement device for improving an axial and radial scroll compliant structure, which is arranged between the orbiting scroll and the base casing to be capable of performing a similar orbiting operation with the orbiting scroll.
  • the thrust bearing forms a sealed pressure chamber by contacting the sealing element between the orbiting scroll and the orbiting thrust bearing, creating a biasing force that causes the orbiting scroll to axially follow the fixed scroll.
  • Figure 1 is a longitudinal sectional view showing an example of a scroll expander having a single scroll structure
  • Figure 2 is a longitudinal schematic view of a scroll type volume displacement device with an orbiting thrust bearing of the present invention
  • Figure 3 is a transverse cross-sectional view taken along line 3-3 of the middle of Figure 2; A mechanism for driving a orbiting thrust bearing by an orbiting scroll is shown;
  • Figure 4 is a longitudinal sectional view taken along line 4-4 of Figure 3. The difference from Fig. 2 is that the section is rotated by 90° along the main axis S1-S1;
  • Figure 5 is a longitudinal cross-sectional view showing a scroll type displacement device with a bidirectional winding type thrust bearing according to the present invention
  • Figure 6 is a cross-sectional view showing a bidirectional thrust bearing mechanism of a scroll type displacement device with a two-way orbiting thrust bearing according to the present invention
  • Figure 6A is a schematic view of the upper thrust bearing of the double-way thrust bearing mechanism of Figure 6;
  • Figure 6B is a schematic view of the fixed thrust bearing of the double-way thrust bearing mechanism of Figure 6;
  • Figure 6C is a schematic view of the lower thrust bearing of the double direction thrust bearing mechanism of Figure 6. detailed description
  • FIG. 2 is a longitudinal cross-sectional view of a scroll type displacement device with an orbiting thrust bearing according to the present invention, as shown in FIG. 2, a scroll type displacement device 10 with an orbiting thrust bearing, including A main housing 20, a base housing 70, a rotary drive shaft 40, a fixed scroll 50 and an orbiting scroll 60.
  • the fixed scroll 50 has a first end plate 51 on which a scroll element 52 is fixed, and the scroll element 52 is fixed thereon and thereby extends outward;
  • the orbiting scroll 60 has a second The end plate 61, the second end plate 61 is fixedly provided with a scroll element 62, and the scroll element 62 is fixed thereon and thereby extends outward;
  • the first end plate 51 provided with the scroll element 52 and the scroll element are provided
  • the second end plates 61 of 62 are adjacent to each other such that the scroll element 52 and the scroll element 62 are in mesh with each other, and the scroll element 52 and the scroll element 62 are respectively abutted against the second end plate 61 and the first end plate 51.
  • the fixed scroll 50 and the orbiting scroll 60 are respectively disposed in the main casing 20, and the fixed scroll 50 is supported by the main casing 20, and the end plate 51 of the fixed scroll 50 is integrated with the main casing 20, and the base
  • the casing 70 is coupled to the main casing 20, and the base casing 70 faces the rear end of the orbiting scroll 60.
  • a rotary drive shaft 40 includes a central shaft 41, a crankshaft 42 disposed at one end of the central shaft 41, a central shaft 41 extending through the intermediate portion of the base housing 70, and having a rear end of the crankshaft 42 adjacent the orbiting scroll 60
  • the crankshaft 42 can drive the orbiting bearing seat 63 at the rear of the orbiting scroll 60 through the joint 64 crankshaft bearing 260, thereby driving the orbiting scroll 60 to make a circular translation with respect to the fixed scroll 50, that is, orbiting;
  • the front and rear portions of the shaft 41 are respectively supported by a bearing 33 and a bearing 34.
  • the bearing 33 and the bearing 34 are respectively disposed on the base casing 70, and are supported by the base casing 70 such that the central shaft 41 is rotatably disposed in the base casing. In 70, the positioning of the center shaft 41 is simultaneously performed by the bearing 33 and the bearing 34. In There is also a motor 35 between the bearing 33 and the bearing 34. The motor 35 is located in the base casing 70 and supported by the base casing 70. The central shaft 41 penetrates the motor 36 so that the central shaft 41 can be driven by the motor 35. The axis SI-S1 rotates.
  • an air inlet 80 in the main housing 20.
  • an intake passage 81 through which a working fluid such as air can enter the intake passage 81 through the intake port 80 on the main casing 20.
  • a central air chamber 82 is disposed in a middle portion between the orbiting scroll 60 and the fixed scroll 50, and a pressure chamber 83 is provided between the rear end surface of the orbiting scroll 60 and the orbiting thrust bearing 172, and is properly fixed.
  • the pressure gas introduced by the pressure chamber between the scroll 50 and the orbiting scroll 60 communicates with the pressure chamber 83 through a suitable passage 88; the working fluid entering the suction passage 81 is sucked into the fixed scroll 50 and the orbiting
  • the pressure chamber formed between the scrolls 60 is compressed in the orbiting motion of the orbiting scroll 60, then transmitted to the central air chamber 82, and finally passed through the central portion of the first end plate 51 of the fixed scroll 50.
  • the exhaust port 84 is discharged outward.
  • Figure 3 is a transverse cross-sectional view taken along line 3-3 of Figure 2, showing the mechanism of the orbiting scroll bearing the orbiting thrust bearing, and the center-driven crankshaft of the present invention shown in Figures 2 and 3; - a sliding joint and a peripheral crank pin - a mechanism for coupling the swing connection mechanism (CSPS structure), including a central drive joint 64, a crank pin bearing 260, a peripheral portion 160a, a bearing hole 161a, a fixed crank 162a, a crank joint bearing 163a, eccentric Hole 166a, peripheral portion 170a, bearing hole 171a, fixed crank 172a, fixed crank bearing 173a, fixed crank bearing 174a, crank pin 175a, eccentric hole 176a, synchronizer 177, synchronizer bearing 177a, synchronizer bearing 177b, synchronizer bearing
  • the composition of parts such as 177c provides the axial and radial compliance movement for the orbiting scroll.
  • the patent number granted to the inventor is ZL200610121150. 3
  • Figure 4 is a longitudinal sectional view taken along line 4-4 of Figure 3, and the difference from Figure 2 is that the section is rotated by 90° along the main axis S1-S1, as shown in Figures 2, 3 and 4.
  • the orbiting thrust bearing 172 is coupled to the orbiting scroll 60 end plate 93 by pins 95a and 95b.
  • the orbiting thrust bearing 172 is in sliding engagement with the pins 95a and 95b.
  • the orbiting thrust bearing 172 is driven to move around by the pins 95a and 95b.
  • a fixed thrust bearing is further included between the second end plate 61 of the orbiting scroll 60 and the base casing 70.
  • the fixed thrust bearing is coupled to the orbiting thrust bearing 172 such that the axial thrust of the orbiting thrust bearing 172 is Fixed thrust bearing bearing.
  • the fixed thrust bearing includes a fixed thrust ball bearing 104 and a orbiting thrust ball bearing 102.
  • the fixed thrust ball bearing 104 is disposed on the base casing 70, and the orbiting thrust ball bearing 102 acts on the fixed thrust ball bearing 104, and at the same time, The thrust ball bearing 102 performs a similar orbiting motion with respect to the fixed thrust ball bearing 104.
  • a sealed pressure plenum 83 formed by a sealing member 90 and a sealing member 92 (for example, an O-ring, a lip seal, etc.), pressure
  • the pressure of the plenum 83 acts on the second end plate 61 of the orbiting wrap 60 such that the orbiting wrap 60 makes a compliant movement relative to the fixed wrap 50. Since the orbiting thrust bearing 172 makes a very similar orbiting with the orbiting scroll 60, there is little relative movement between the sealing members 90 and 92 and the orbiting scroll end plate 93 and the orbiting thrust bearing 172, thereby reducing Wear and friction power loss of the sealing element.
  • the three pairs of double thrust ball bearing mechanisms (only one pair is shown in Fig. 2, the fixed thrust ball bearing 104 and the orbiting thrust ball bearing 102) support the axial thrust of the orbiting thrust ball bearing 172, and the orbiting thrust ball Bearing 172 performs a similar orbital motion as orbiting scroll 60.
  • the orbiting thrust bearing 172 is a bidirectional orbiting thrust bearing, axial thrust can be received in both the axial forward and rearward directions.
  • Figure 5 is a longitudinal cross-sectional view showing a scroll type displacement device with a bidirectional thrust bearing in accordance with the present invention.
  • the structure of the fixed scroll 50 and the orbiting scroll 60 shown in the drawing is the same as that of the specific embodiment 1 which has been described in detail above, and therefore will not be described again.
  • Figure 6 is a cross-sectional view showing a bidirectional thrust bearing mechanism of a scroll type displacement device with a bidirectional thrust type thrust bearing according to the present invention
  • Fig. 7A is a schematic view of the upper thrust bearing of the bidirectional thrust bearing mechanism of Fig. 7
  • Figure 7C is a schematic view of the thrust bearing of the double-way thrust bearing mechanism of Figure 7
  • Figure 7C is a schematic view of the lower thrust bearing of the double-way thrust bearing mechanism of Figure 7, see Figure 5, Figure 6, Figure 6A, Figure 6B and Figure 6C .
  • the fixed thrust bearing includes a lower thrust bearing 74, a fixed bearing 73, and an upper thrust bearing 72.
  • the upper thrust bearing 72 is specifically a disc shape, and the upper thrust bearing 72 has a through hole 72a in the middle thereof, and the upper thrust bearing 72 is provided with three stepped holes 72b and three screw holes 72c.
  • the fixed bearing 73 is specifically a disc shape, and has a through hole 73a in the middle of the fixed bearing 73, a stepped hole 73b concentrically disposed on the periphery of the through hole 73a, and three countersunk screw holes 73c and three are uniformly arranged around the fixed bearing 73.
  • the holes 73d; the three countersunk screws 77 respectively fix the fixed bearing 73 to the base casing 70 through the three holes 73c.
  • the lower thrust bearing 74 is specifically a disc shape having a through hole 74a in the middle of the lower thrust bearing 74, and the lower thrust bearing 74 is provided with three countersunk screw holes 74b and three holes 74c.
  • the upper thrust bearing 72, the fixed bearing 73 and the lower thrust bearing 74 are arranged in order.
  • the three spacers 75 separate the upper thrust bearing 72 and the lower thrust bearing 74 from the thickness of the fixed bearing 73; the three countersunk screws 76 secure the upper thrust bearing 72 and the lower thrust bearing 74 together.
  • the upper thrust bearing 72 and the lower thrust bearing 74 are also fixedly coupled to the orbiting drive bearing 261, and the inner diameter of the orbiting drive bearing 261 is in sliding engagement with the drive bearing 65.
  • the difference between the diameter of the spacer 75 and the diameter of the hole 73d of the fixed bearing 73 is equal to twice the radius of the orbiting wrap 60, that is, the orbiting diameter, while the shaft line S1-S1 of the crank pin 42 and the crank pin
  • the distance of the axis line S2-S2 of 44 is also equivalent to the orbiting radius of the orbiting scroll 60.
  • the axial thrust of the orbiting thrust bearing 172 is received by the upper thrust bearing 72 and the lower thrust bearing 74.
  • a sealing member 90 and a sealing member 93 on the second end plate 61 and the sealing member 90 and the sealing member 93 may employ, for example, a lip seal or a 0-ring or the like between the upper thrust bearing 72 and the second end plate 61.
  • the intake end is at atmospheric pressure and the exhaust end is at atmospheric pressure.
  • the gas pressure in the pressure chamber 83 is higher than atmospheric pressure, and an axial force in the backward (i.e., motor direction) is applied to the orbiting scroll 60.
  • the size of the sealing member 90 and the sealing member 93 is selected to define the area of the pressure plenum 83, and the pressure gas introduced from the compressed plenum of the scroll acts on the rear end of the second end plate 61 of the orbiting scroll 60 plus
  • the elastic preload force applied by the sealing member 90 and the sealing member 93 exceeds the axial separation force applied by the compressed gas at the front end of the orbiting wrap 60, which axially urges the orbiting wrap 60 axially toward
  • the scroll 50 is fixed to obtain a slight contact of the two engagement scrolls, thereby also maintaining a good radial seal between the pressure chambers.
  • the mechanism (CSPS structure) having a center-driven crankshaft-sliding joint and a peripheral crankpin-swinging joint mechanism in the present invention also causes the orbiting scroll element 62 to radially maintain contact with the fixed scroll element 52, Maintain a tangential seal of the compressed air chamber.
  • the upper thrust bearing 72 moves to the rear, i.e., the motor direction, in sliding contact with the fixed bearing 73, and the latter receives the axial thrust.
  • the suction end pressure gradually decreases, the gas pressure in the pressure chamber is lower than atmospheric pressure, and the subatmospheric pressure gas introduced from the compressed air chamber of the scroll acts on the second end of the orbiting scroll 60.
  • the force at the rear end of the plate 61 plus the elastic preload applied by the sealing member 90 and the sealing member 93 plus the combined force of the atmospheric pressure applied to all of the outer surfaces of the non-closed plenum of the orbiting scroll 60 will The orbiting scroll 60 is axially urged toward the fixed scroll 50 to obtain a slight contact of the two engaging scrolls.
  • the invention relates to a scroll type displacement device with an orbiting thrust bearing, which is intended to provide a thrust ball bearing capable of orbiting the orbiting scroll between the orbiting scroll and the base casing, and adopting multiple sets of thrust
  • the ball bearing balances the possible sloshing in the orbiting motion of the orbiting scroll and passes the orbiting scroll and the thrust ball shaft
  • the sealing contact generated between the bearings seals the pressure chamber by the axial biasing force of the orbiting scroll; at the same time, the pressure chamber passes through the seal therein to maintain a slight contact with the front and rear end faces of the two-phase engaging scroll.

Landscapes

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

Abstract

一种带有绕动式推力轴承的涡卷式容积位移装置，固定涡卷（50）的第一端板（51）的涡卷元件（52）与绕动涡卷（60）的第二端板（61）的涡卷元件（62）相啮合，固定涡卷（50）和绕动涡卷（60）分别设置在主壳体（20）中，底座机壳（70）与主壳体（20）连接；旋转驱动轴（40）贯穿底座机壳（70）的中间部分，并且靠近绕动涡卷（60）的后端；一绕动推力轴承（172）通过销子（95a，95b）与绕动涡卷轴承座端板（93）连接，同时，绕动推力轴承（172）做与绕动涡卷（60）相似的绕动运动。该装置旨在绕动涡卷（60）与底座机壳（70）之间设置能够沿绕动涡卷（60）做轨道运行的推力球轴承，通过多组推力球轴承以平衡在绕动涡卷（60）做轨道运动中可能产生的晃动，并且通过绕动涡卷（60）与推力球轴承之间产生的密封接触，将绕动涡卷（60）的轴向偏向力对压力气室（83）进行密封，从而保持对两相啮合涡卷前后端面的轻微接触。

Description

一种带有绕动式推力轴承涡卷式容积位移装置 技术领域
本发明涉及一种涡卷式容积位移装置， 尤其涉及一种提高轴向和径向涡卷 依从结构的涡卷式容积位移装置。 背景技术
在机械领域，涡卷式流体位移装置用于压缩机和膨胀机，涡卷是在一个端板 上延伸出一个具有螺旋剖面的柱面的元件。通常一个是固定的， 叫做定涡卷。另 一个涡卷具有与定涡卷的螺旋柱面相共轭的螺旋柱面，并相对于定涡卷做圆形的 平动， 也叫绕动， 被称为绕动涡卷。
这两种涡卷的互相共轭的螺旋式涡卷柱面相互啮合形成线接触。
一对线接触与端板表面之间至少形成一密封气室。当一个绕动涡卷相对于固 定涡卷做轨道运动（圆周运动）时，在螺旋型侧壁上的线接触会沿着该侧壁移动， 从而改变密封气室的大小。 而轨道运动的方向将决定密封气室膨胀或是压缩流 体。
美国专利号 7467933， 图 1为一种具有单涡卷结构的涡卷膨胀机的实例的纵 向剖面图，请参见图 1所示，一种具有单涡卷结构的涡卷膨胀机的实例的纵剖面 图， 涡卷装置 10包括一主壳体 20, 底座机壳 70， 旋转驱动轴 40， 固定涡卷 50 和绕动涡卷 60，绕动涡卷 60具有一第二端板 61 ;底座机壳 70与主壳体 20相连 接， 主壳体 20中设置固定涡卷 50和绕动涡卷 60， 在底座机壳 70的前端具有推 力轴承 71， 推力轴承 71与绕动涡卷 60的第二端板 61的后端的密封凸台 64之 间有滑动摩擦的接触并在密封凸台 64同推力轴承 71的前平面之间形成一压力气 室 83， 压缩气体进入压力气室 83, 使得压力气室 83产生轴向偏向力， 将绕动涡 卷 60沿轴向推向固定涡卷 50。
实现密封元件的密闭接触是在绕动涡卷上设置一至多个如密封凸台和密封 圈等的密封元件。但是这种方法有这样两个问题， 一是， 密封元件随着绕动涡卷 做轨道运行时，由于绕动涡卷在各种力和力矩的作用下做轨道运行时会作绕垂直 于主轴 SI- S1的轴线的晃动， 如同图 1中 N-N所示， 使得密封凸台 64与推力轴 承 71的密封接触易松动。二是，在无油状态下 作绕动运动的密封元件和推力轴 承之间做滑动接触时会产生摩擦功率损失和密封元件的磨损。 发明内容
本发明提供了一种具有能提高涡卷轴向依从结构的可靠性和提高涡卷装置 能量效率的机构的涡卷式容积位移装置，其具有做与绕动涡卷相似的绕动运动的 推力轴承，使得绕动涡卷与推力轴承之间基本上无相对运动，绕动涡卷的背面与 绕动推力轴承之间通过密封元件（例如密封凸台， 0形圈， 唇封等）产生密封接 触从而形成密封的压力气室。绕动推力轴承与绕动涡卷之间的压力气室的气体压 力与密封原件的弹性力，及其他力产生的对绕动涡卷的轴向偏向力使绕动涡卷对 固定涡卷作轴向依从运动。这样密封元件的寿命和可靠性和磨擦功率损耗得到改 善。
一种带有绕动式推力轴承涡卷式容积位移装置，包括一主壳体、一底座机壳、 一固定涡卷和一绕动涡卷； 其中： 还包括有一绕动推力轴承， 所述绕动推力轴承 通过销子和销子与所述绕动涡卷的轴承座端板连接，所述绕动推力轴承做与所述 绕动涡卷相似的绕动运动。
进一步的，所述绕动推力轴承与所述销子和所述销子为滑动配合，所述绕动 涡卷通过所述销子和所述销子带动所述绕动推力轴承运动。
进一步的，所述绕动涡卷具有一第二端板，所述绕动推力轴承与所述绕动涡 卷的第二端板之间形成密闭的压力气室，所述压力气室的压力作用在所述绕动涡 卷的第二端板上， 使得所述绕动涡卷做相对于所述固定涡卷的依从运动。
进一步的，所述绕动涡卷的第二端板和所述底座机壳之间还包括有固定推力 轴承，所述固定推力轴承与所述绕动推力轴承连接，使得所述绕动推力轴承所受 的轴向推力由所述固定推力轴承承受。 进一步的，所述固定推力轴承包括固定推力球轴承和绕动推力球轴承，所述 固定推力球轴承设置在所述底座机壳上，所述绕动推力球轴承作用在所述固定推 力球轴承上， 同时，所述绕动推力球轴承相对于所述固定推力球轴承做相似的绕 动运动。
更进一步的，所述绕动推力轴承的轴向推力由所述固定推力球轴承和所述绕 动推力球轴承承受。
本发明提供的一种提高轴向和径向涡卷依从结构的涡卷式容积位移装置，其 在绕动涡卷与底座机壳之间设置能够与绕动涡卷做相似的绕动运行的推力轴承， 通过绕动涡卷与绕动推力轴承之间的密封元件接触，形成密封的压力气室，产生 使绕动涡卷对固定涡卷的轴向依从的偏向力。 附图说明
图 1是一种具有单涡卷结构的涡卷膨胀机的实例的纵向剖面图； 图 2 是本发明一种带有绕动式推力轴承的涡卷式容积位移装置的纵向示意 图；
图 3是图 2的中沿 3-3线的横向剖面图。显示了由绕动涡卷带动绕动式推力 轴承的机构；
图 4是图 3 中沿 4-4线的纵向剖面图。 与图 2的不同之处是剖面沿主轴线 S1-S1旋转了 90°;
图 5 为本发明一种带有双向的绕动式推力轴承的涡卷式容积位移装置的纵 向剖视图；
图 6 是本发明一种带有双向的绕动式推力轴承的涡卷式容积位移装置的双 向推力轴承机构的剖视图；
图 6A是图 6中双向推力轴承机构的上推力轴承的示意图；
图 6B是图 6中双向推力轴承机构的固定推力轴承的示意图；
图 6C是图 6中双向推力轴承机构的下推力轴承的示意图。 具体实施方式
以下结合附图给出本发明一种带有绕动式推力轴承涡卷式容积位移装置的 具体实施方式 1。
图 2为本发明一种带有绕动式推力轴承涡卷式容积位移装置的纵向剖面图， 请参见图 2所示， 一种带有绕动式推力轴承涡卷式容积位移装置 10， 包括一主 壳体 20， 一底座机壳 70， 一旋转驱动轴 40， 一固定涡卷 50和一绕动涡卷 60。 固定涡卷 50具有一第一端板 51， 在第一端板 51上固定设有涡卷元件 52， 涡卷 元件 52固定其上并由此向外延伸； 绕动涡卷 60具有一第二端板 61， 第二端板 61上固定设有涡卷元件 62，涡卷元件 62固定其上并由此向外延伸； 设有涡卷元 件 52的第一端板 51与设有涡卷元件 62的第二端板 61相互靠近，使得涡卷元件 52与涡卷元件 62之间相互啮合， 并且涡卷元件 52与涡卷元件 62分别抵于第二 端板 61和第一端板 51上， 并保持 180° 的相位角位移和等于绕动半径 Ror的径 向位移。 当绕动涡卷 60相对于固定涡卷 50做绕动运动时， 涡卷元件 52和涡卷 元件 62之间至少形成一个密封的气室， 通过第一端板 51和第二端板 61啮合面 之间的滑动来改变气室的容积。
通过绕动涡卷做相对于固定涡卷圆形平动 （即绕动） 时， 能够造成对第一 端板侧壁和第二端板侧壁之间的移动的线接触。
固定涡卷 50和绕动涡卷 60分别设置在主壳体 20中，通过主壳体 20来支撑 固定涡卷 50， 且固定涡卷 50的端板 51与主壳体 20合为一体， 底座机壳 70与 主壳体 20连接， 底座机壳 70正对绕动涡卷 60的后端。
一旋转驱动轴 40包括一中央轴 41， 一曲轴 42， 曲轴 42设置在中央轴 41 的一端， 中央轴 41贯穿底座机壳 70的中间部分， 且具有曲轴 42靠近绕动涡卷 60的后端，曲轴 42通过关节 64曲轴轴承 260 能够带动绕动涡卷 60后部的绕动 轴承座 63， 从而带动绕动涡卷 60作相对于固定涡卷 50的圆形平动， 即绕动； 中央轴 41的前后两部分别由轴承 33和轴承 34所支撑， 轴承 33和轴承 34分别 设置在底座机壳 70， 并且由底座机壳 70所支撑， 使得中央轴 41可转动地设置 在底座机壳 70中， 同时通过轴承 33和轴承 34起到对中央轴 41定位的作用。在 轴承 33和轴承 34之间还具有一马达 35， 马达 35位于底座机壳 70中， 并且由 底座机壳 70所支撑， 中央轴 41贯通马达 36，使得在马达 35的驱动下中央轴 41 能够绕轴线 SI- S1转动。
在主壳体 20上具有一进气口 80。在主壳体 20与固定涡卷 50和绕动涡卷 60 之间具有一吸气通道 81， 当工作流体例如空气， 能够通过主壳体 20上的进气口 80进入吸气通道 81。 在绕动涡卷 60和固定涡卷 50之间的中部具有一中央气室 82，绕动涡卷 60的后端面与绕动推力轴承 172 之间具有一压力气室 83， 从适当 的位于固定涡卷 50和绕动涡卷 60之间的压力气室引入的压力气体通过适当的通 道 88与压力气室 83相连通； 进入吸气通道 81的工作流体被吸入在固定涡卷 50 和绕动涡卷 60之间形成的压力气室，并在绕动涡卷 60的绕动运动中被压缩，然 后传递至中央气室 82， 最后通过位于固定涡卷 50的第一端板 51中央部位的排 气口 84向外排出。
图 3是图 2的中沿 3-3线的横向剖面图，为绕动涡卷带动绕动式推力轴承的 机构的示意图，图 2和图 3所示的本发明的具有中心驱动曲柄轴——滑动关节与 周边曲柄销——摆动连接机构相结合的机构 (CSPS结构），包括中央驱动关节 64、 曲轴销轴承 260、 周边部分 160a、 轴承孔 161a、 固定曲柄 162a、 曲柄关节轴承 163a,偏心孔 166a、 周边部分 170a、 轴承孔 171a、 固定曲柄 172a、 固定曲柄轴 承 173a、 固定曲柄轴承 174a、 曲柄销 175a、 偏心孔 176a、 同步器 177、 同步器 轴承 177a、 同步器轴承 177b、 同步器轴承 177c等零件组成， 为绕动涡卷提供了 轴向和径向作依从运动的能力， 系沿用了授予本发明人的专利号为 ZL200610121150. 3 题为 "改进的具有全依从浮动涡卷的涡卷型容积式压缩机" 的中国专利， 在此不再赘述。
图 4是图 3 中沿 4-4线的纵向剖面图， 与图 2的不同之处是剖面沿主轴线 S1-S1旋转了 90°， 请参看看图 2、 图 3和图 4所示。绕动推力轴承 172通过销子 95a和 95b与绕动涡卷 60轴承座端板 93相连。 绕动推力轴承 172与销子 95a和 95b为滑动配合。绕动涡卷 60作绕动运动时通过销子 95a和 95b带动绕动推力轴 承 172 作绕动运动。 在绕动涡卷 60的第二端板 61和底座机壳 70之间还包括有固定推力轴承， 固定推力轴承与绕动推力轴承 172连接，使得绕动推力轴承 172所受的轴向推力 由固定推力轴承承受。该固定推力轴承包括固定推力球轴承 104和绕动推力球轴 承 102， 固定推力球轴承 104设置在底座机壳 70上， 绕动推力球轴承 102作用 在固定推力球轴承 104上， 同时， 绕动推力球轴承 102相对于固定推力球轴承 104做相似的绕动运动。
绕动推力轴承 172与绕动涡卷 60的端板 61的后部之间有由密封元件 90和 密封元件 92 (例如： 0型圈、 唇封等）所形成的密封压力气室 83， 压力气室 83 的压力作用在绕动涡卷 60的第二端板 61上， 使得绕动涡卷 60做相对于固定涡 卷 50的依从运动。 由于绕动推力轴承 172做与绕动涡卷 60极其相似的绕动， 因 而密封元件 90和 92与动涡卷轴承座端板 93和绕动推力轴承 172之间只有极少 相对运动，从而减少了密封元件的磨损和摩擦功率损失。三对双推力球轴承机构 (图 2只画出一对， 固定推力球轴承 104和绕动推力球轴承 102 )支承了绕动推 力球轴承 172所承受的轴向推力， 并使绕动推力球轴承 172做与绕动涡卷 60相 似的轨道运动。而且， 由于绕动推力轴承 172是一双向绕动推力轴承， 使得能在 轴向的向前和向后两个方向上承受轴向推力。
以下结合附图给出本发明一种带有绕动式推力轴承涡卷式容积位移装置的 具体实施方式 2。
图 5 为本发明一种带有双向的绕动推力轴承的涡卷式容积位移装置的纵向 剖视图。 图中所示的固定涡卷 50和绕动涡卷 60 的结构， 工作原理度与上面已 详细描述的具体实施方案 1是一样的， 故不再赘述。
图 6 为本发明一种带有双向的绕动式推力轴承的涡卷式容积位移装置的双 向推力轴承机构的剖视图， 图 7A为图 7中双向推力轴承机构的上推力轴承的示 意图， 图 7B为图 7中双向推力轴承机构的固定推力轴承的示意图， 图 7C为图 7 中双向推力轴承机构的下推力轴承的示意图， 请参见图 5、 图 6、 图 6A、 图 6B 和图 6C所示。在绕动涡卷 60的第二端板 61和底座机壳 70之间具有固定推力轴 承， 该固定推力轴承包括下推力轴承 74、 固定轴承 73和上推力轴承 72。通过驱 动轴承 65和绕动驱动轴承 261带动上推力轴承 72和下推力轴承 74做与绕动涡 卷 60相似的绕动。
上推力轴承 72具体为一圆盘形， 上推力轴承 72的中间具有一通孔 72a, 上 推力轴承 72的四周均布三个台阶孔 72b和三个螺纹孔 72c。
固定轴承 73具体为一圆盘形， 在固定轴承 73的中间具有一通孔 73a， 在通 孔 73a的外围同心设置有一台阶孔 73b， 固定轴承 73的四周均布三个沉头螺钉 孔 73c 和三个孔 73d; 三个沉头螺钉 77分别穿过三个孔 73c将固定轴承 73 固 定在底座机壳 70上。
下推力轴承 74具体为一圆盘形， 在下推力轴承 74的中间具有一通孔 74a， 下推力轴承 74的四周均布有三个沉头螺钉孔 74b和三个孔 74c。
上推力轴承 72， 固定轴承 73和下推力轴承 74依次排列。 三个隔套 75把上 推力轴承 72和下推力轴承 74隔开， 使其距离比固定轴承 73的厚度大； 三个沉 头螺钉 76将上推力轴承 72和下推力轴承 74固联在一起，上推力轴承 72和下推 力轴承 74还与绕动驱动轴承 261固联在一起， 且绕动驱动轴承 261的内径与驱 动轴承 65采用滑动配合。 隔套 75的直径与固定轴承 73的孔 73d的直径之差等 于绕动涡卷 60的绕动半径的两倍，即为绕动直径，同时曲轴销 42的轴心线 S1-S1 和曲轴销 44的的轴心线 S2- S2的距离也等同于绕动涡卷 60的绕动半径。当曲轴 销 44带动驱动轴承 65， 再带动绕动驱动轴承 261 , 并最终使得上推力轴承 72 和下推力轴承 74做绕动运动， 同时绕动驱动轴承 261、 上推力轴承 72和下推力 轴承 74能够一起做轴向的滑动。安装于孔 73d中的隔套 75则有效地起到防止上 推力轴承 72和下推力轴承 74做转动。
最终，绕动推力轴承 172的轴向推力由上推力轴承 72和下推力轴承 74承受。 在第二端板 61上具有密封元件 90和密封元件 93，密封元件 90和密封元件 93可采用例如唇形密封圈或者 0型密封圈等， 在上推力轴承 72和第二端板 61 之间还具有一压力气室 83， 通过密封元件 90和密封元件 93将压力气室 83与周 围区域密封区隔。涡卷装置启动时，密封元件 90和密封元件 93的弹性预紧力保 证绕动涡卷 60推向固定涡卷 50时两相啮合的涡卷之间具有轻微的轴向接触。在 涡卷装置运行时位于固定涡卷 50和绕动涡卷 60之间压力气室中的压力能够通过 通道与压力气室 83相连通。
在真空泵的应用中， 在启动时进气端处于大气压，排气端也处于大气压。压 力气室 83中的气体压力高于大气压，对绕动涡卷 60施加一个向后（即马达方向） 的轴向力。 密封元件 90和密封元件 93的尺寸选定，确定了压力气室 83的面积， 从涡卷的压缩气室引入的压力气体作用在绕动涡卷 60第二端板 61的后端的力加 上由密封元件 90和密封元件 93所施加的弹性预紧力超过由被压缩气体在绕动涡 卷 60的前端施加的轴向分离力，此轴向合力将绕动涡卷 60沿轴向推向固定涡卷 50以得到两啮合涡卷的轻微接触， 从而也使压力气室之间保持良好的径向密封。 本发明中具有中心驱动曲柄轴——滑动关节与周边曲柄销——摆动连接机构相 结合的机构 （CSPS结构） 也使得绕动涡卷元件 62径向保持与固定涡卷元件 52 的接触， 以保持压缩气室的切向密封。此时在压力气室 83中的气体压力作用下， 上推力轴承 72 向后部， 即马达方向移动而与固定轴承 73作滑动接触， 由后者 承受起轴向的推力。
当涡卷真空泵继续运转，吸气端压力逐步下降，压力气室中的气体压力低于 大气压， 从涡卷的压缩气室引入的低于大气压的压力气体作用在绕动涡卷 60第 二端板 61的后端的力加上由密封元件 90和密封元件 93所施加的弹性预紧力加 上作用在绕动涡卷 60的非密闭气室的所有外表面所受的大气压力的合力， 将绕 动涡卷 60沿轴向推向固定涡卷 50以得到两啮合涡卷的轻微接触。此时作用在上 推力轴承 72背面的大气压力会将上推力轴承 72和下推力轴承 74向前 （固定涡 卷方向） 推， 此时上推力轴承 72和下推力轴承 74向前部移动， 被固定轴承 73 所阻挡， 而下推力轴承 74的前面（朝向固定涡卷方向）与固定轴承 73的后面作 滑动接触， 由后者承受起轴向的推力，避免由于大气压和真空之间的压力差造成 过大的作用在动涡卷上的轴向推力。
本发明一种带有绕动式推力轴承涡卷式容积位移装置，其旨在绕动涡卷与底 座机壳之间设置能够沿绕动涡卷做轨道运行的推力球轴承，通过多组推力球轴承 以平衡在绕动涡卷做轨道运动中可能产生的晃动，并且通过绕动涡卷与推力球轴 承之间产生的密封接触，将绕动涡卷的轴向偏向力对压力气室进行密封； 同时压 力气室通过其中的密封件能够保持对两相啮合涡卷前后端面的轻微接触。

Claims

权 利 要 求 书
1. 一种带有绕动式推力轴承涡卷式容积位移装置， 包括一主壳体（20)、 一底座 机壳（70)、 一固定涡卷（50)和一绕动涡卷（60);
其特征在于： 还包括有一绕动推力轴承 （172)， 所述绕动推力轴承 （172 ) 通过销子（95a)和销子（95b)与所述绕动涡卷（60)的轴承座端板（93)连接， 所述绕动推力轴承 （172) 做与所述绕动涡卷（60) 相似的绕动运动。
2.根据权利要求 1所述带有绕动式推力轴承涡卷式容积位移装置，其特征在于: 所述绕动推力轴承 （172 ) 与所述销子 （95a)和所述销子 （95b) 为滑动配 合， 所述绕动涡卷（60)通过所述销子（95a)和所述销子（95b )带动所述绕动 推力轴承 （172) 运动。
3.根据权利要求 1所述带有绕动式推力轴承涡卷式容积位移装置，其特征在于: 所述绕动涡卷（60)具有一第二端板（61 )， 所述绕动推力轴承（172)与所 述绕动涡卷 （60) 的第二端板 （61 ) 之间形成密闭的压力气室 （83 ) , 所述压力 气室（83) 的压力作用在所述绕动涡卷（60) 的第二端板（61 )上， 使得所述绕 动涡卷 （60) 做相对于所述固定涡卷（50) 的依从运动。
4.根据权利要求 1所述带有绕动式推力轴承涡卷式容积位移装置，其特征在于: 所述绕动涡卷（60)的第二端板（61 )和所述底座机壳（70)之间还包括有 固定推力轴承， 所述固定推力轴承与所述绕动推力轴承 （172 ) 连接， 使得所述 绕动推力轴承 （172 )所受的轴向推力由所述固定推力轴承承受。
5.根据权利要求 4所述带有绕动式推力轴承涡卷式容积位移装置，其特征在于: 所述固定推力轴承包括固定推力球轴承 （104) 和绕动推力球轴承 （102)， 所述固定推力球轴承 （104) 设置在所述底座机壳 （70)上， 所述绕动推力球轴 承（102 )作用在所述固定推力球轴承（104)上，同时，所述绕动推力球轴承（102) 相对于所述固定推力球轴承 （104)做相似的绕动运动。
6.根据权利要求 5所述带有绕动式推力轴承涡卷式容积位移装置，其特征在于： 所述绕动推力轴承（172 )的轴向推力由所述固定推力球轴承（104)和所述 绕动推力球轴承 （102 ) 承受。
PCT/CN2012/000772 2011-06-07 2012-06-06 一种带有绕动式推力轴承涡卷式容积位移装置 WO2012167610A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/124,321 US20140140877A1 (en) 2011-06-07 2012-06-06 Scroll-type volume displacement apparatus with an orbiting thrust bearing

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201110150716.6 2011-06-07
CN201110150716.6A CN102817840B (zh) 2011-06-07 2011-06-07 一种带有绕动式推力轴承的涡卷式容积位移装置

Publications (1)

Publication Number Publication Date
WO2012167610A1 true WO2012167610A1 (zh) 2012-12-13

Family

ID=47295426

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2012/000772 WO2012167610A1 (zh) 2011-06-07 2012-06-06 一种带有绕动式推力轴承涡卷式容积位移装置

Country Status (3)

Country Link
US (1) US20140140877A1 (zh)
CN (1) CN102817840B (zh)
WO (1) WO2012167610A1 (zh)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI609143B (zh) * 2016-12-29 2017-12-21 財團法人工業技術研究院 偏心擺動減速裝置
KR20180136282A (ko) 2017-06-14 2018-12-24 엘지전자 주식회사 원심 및 차압 급유 구조가 구비된 압축기
KR102396559B1 (ko) 2017-06-22 2022-05-10 엘지전자 주식회사 스러스트면 윤활 구조가 구비된 압축기
KR102440273B1 (ko) * 2017-06-23 2022-09-02 엘지전자 주식회사 토출 성능을 개선한 압축기
US20200088193A1 (en) * 2017-08-25 2020-03-19 Mitsubishi Heavy Industries, Ltd. Co-rotating scroll compressor
JP6842385B2 (ja) 2017-08-25 2021-03-17 三菱重工サーマルシステムズ株式会社 スクロール圧縮機

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4160629A (en) * 1977-06-17 1979-07-10 Arthur D. Little, Inc. Liquid immersible scroll pump
CN1111725A (zh) * 1993-11-19 1995-11-15 倪诗茂 高压缩比涡卷容积式流体位移装置
US5616015A (en) * 1995-06-07 1997-04-01 Varian Associates, Inc. High displacement rate, scroll-type, fluid handling apparatus
CN101008321A (zh) * 2006-01-26 2007-08-01 倪诗茂 改进的具有全方位依从悬浮涡卷的涡卷流体位移装置
CN100410537C (zh) * 2002-04-11 2008-08-13 倪诗茂 具有全方位依从结构的悬浮式涡卷型流体压缩装置

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3399380B2 (ja) * 1998-10-12 2003-04-21 株式会社デンソー 圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4160629A (en) * 1977-06-17 1979-07-10 Arthur D. Little, Inc. Liquid immersible scroll pump
CN1111725A (zh) * 1993-11-19 1995-11-15 倪诗茂 高压缩比涡卷容积式流体位移装置
US5616015A (en) * 1995-06-07 1997-04-01 Varian Associates, Inc. High displacement rate, scroll-type, fluid handling apparatus
CN100410537C (zh) * 2002-04-11 2008-08-13 倪诗茂 具有全方位依从结构的悬浮式涡卷型流体压缩装置
CN101008321A (zh) * 2006-01-26 2007-08-01 倪诗茂 改进的具有全方位依从悬浮涡卷的涡卷流体位移装置

Also Published As

Publication number Publication date
CN102817840B (zh) 2014-08-27
US20140140877A1 (en) 2014-05-22
CN102817840A (zh) 2012-12-12

Similar Documents

Publication Publication Date Title
US7467933B2 (en) Scroll-type fluid displacement apparatus with fully compliant floating scrolls
WO2012167610A1 (zh) 一种带有绕动式推力轴承涡卷式容积位移装置
JP4709076B2 (ja) 容積形流体機械
JP4584306B2 (ja) スクロール膨張機
KR20080087052A (ko) 스크롤형 유체기계
US6758659B2 (en) Scroll type fluid displacement apparatus with fully compliant floating scrolls
JPH02227581A (ja) スクロール流体機械およびスクロール流体機械用オルダム継手
WO2012167611A1 (zh) 一种带有双向推力轴承的涡卷式容积位移装置
JPH05248371A (ja) スクロール流体機械及びスクロール圧縮機
WO2018020651A1 (ja) スクロール式流体機械及びその組立方法
KR100842301B1 (ko) 일체형 스크롤 팽창기-압축기
JP2001304141A (ja) スクロール型変圧装置
JPH04101089A (ja) スクロール流体機械
JP2864633B2 (ja) スクロール型流体装置
JPS5810586B2 (ja) 容積式流体圧縮装置
JP2003021084A (ja) スクロール型圧縮機
JP2003301784A (ja) スクロール流体機械の自転防止機構
JPS6047442B2 (ja) スクロ−ル機械
JP2001234877A (ja) スクロール圧縮機及びその騒音防止方法
KR102002123B1 (ko) 전동식 압축기
JP2751318B2 (ja) スクロール型圧縮機
JP2004138072A (ja) 回転式スクロール圧縮機
CN1086294A (zh) 改进的涡卷容积式流体位移装置
KR20120081488A (ko) 분리식 선회스크롤을 갖는 스크롤 압축기
KR20120081490A (ko) 분리식 선회스크롤을 갖는 스크롤 압축기

Legal Events

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

Ref document number: 12797127

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 14124321

Country of ref document: US

122 Ep: pct application non-entry in european phase

Ref document number: 12797127

Country of ref document: EP

Kind code of ref document: A1