WO2012167611A1

WO2012167611A1 - Scroll type displacement device having bidirectional thrust bearing

Info

Publication number: WO2012167611A1
Application number: PCT/CN2012/000773
Authority: WO
Inventors: 倪诗茂
Original assignee: 思科涡旋科技(杭州)有限公司
Priority date: 2011-06-07
Filing date: 2012-06-06
Publication date: 2012-12-13
Also published as: CN102817841B; CN102817841A

Abstract

A scroll-type volume displacement device having a bidirectional thrust bearing, comprising a main housing (20), a base housing (70), a rotating drive shaft (40), a fixed scroll (50) and an orbiting scroll (60). Between a second end plate (61) of the orbiting scroll (60) and the base housing (70) are arranged a lower thrust bearing (74), a fixed bearing (73) and an upper thrust bearing (72), said lower thrust bearing (74) and said base housing (70) forming a pressure gas chamber. The upper thrust bearing (72) is connected to the lower thrust bearing (74), and the fixed bearing (73) is disposed on a bearing seat of the base housing (70). The upper thrust bearing (72) and the lower thrust bearing (74) make an orbital motion similar to the orbiting scroll (60). The bidirectional thrust bearing of the present scroll-type volume displacement device allow the orbiting scroll to maintain axial float and slight axial sealing contact with the fixed scroll when axial forces change greatly during the compression process or during the start-up process.

Description

Description of the invention relates to a scroll type volume displacement device with a bidirectional thrust bearing

The present invention relates to a scroll volume displacement device, and more particularly to a scroll volume displacement device having a two-way thrust bearing structure. Background technique

In the mechanical field, scroll-type fluid displacement devices are used in compressors and expanders. Scrolls are components that extend a cylindrical section with a spiral profile on one end plate, usually one fixed, called a fixed scroll, and A scroll has a helical cylinder conjugated to the helical cylinder of the fixed scroll and is circularly translated relative to the fixed scroll, and is called a moving 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. When an orbiting scroll makes orbital motion (circumferential motion) with respect to the fixed scroll, the line contact on the spiral side wall moves along the side wall, thereby changing the size of the sealed air chamber. The direction of the orbital motion will determine whether the sealed chamber expands or compresses the fluid.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view of Fig. 9 of the Chinese patent entitled "Improved scroll-type positive displacement compressor with full-floating floating scroll", which is entitled to the inventor's patent number ZL200610121150. The movement of the orbiting scroll is realized by a piston sealing structure, as shown in FIG. 1, comprising a main housing 20, a base housing 70, a rotating drive shaft 40, a fixed scroll 50 and an orbiting scroll 60; The orbiting wrap 60 has a second end plate 61. The fixed wrap 50 has a first end plate 51. The base casing 70 is connected to the main casing 20. The main casing 20 is provided with a fixed wrap 50 and an orbiting The scroll 60, the base casing 70 and the rear end of the second end plate 61 of the orbiting scroll 60 are formed with a pressure plenum 83, and a sealing mechanism is disposed at the rear end of the base casing 70 and the second end plate 61 for The sealing pressure chamber 83; the sealing mechanism includes an orbiting movable piston 68, a sealing ring 71 and a spring 72, and the movable piston 68 is urged by the spring 72 so that it can axially contact the sealing surface 73 of the base casing 70.

1

Confirmation The hermetic contact of the sealing mechanism is to provide one or more sealing means such as a sealing ring and a piston on the orbiting scroll. However, this method is only applicable to the conventional compressor, that is, the compressed gas in the compressed air chamber between the orbiting scroll and the fixed scroll always tends to wrap the orbiting scroll in the axial direction and the fixed scroll from start to stop. Separation. The spring force of the gas pressure in the sealed pressure chamber is greater than the separation force, maintaining a controlled contact between the orbiting scroll and the fixed scroll. However, when the pressure of the vacuum pump or the sealed compressor casing is higher than the intake pressure of the compressor, the sealed expander may have different conditions. For example, when the vacuum pump is started, the suction end is at atmospheric pressure, the exhaust end is also at atmospheric pressure, and the pressure of the compressed air chamber between the orbiting scroll and the fixed scroll is higher than atmospheric pressure. At this time, the orbiting scroll is axially received. Separation force. When the vacuum pump is started, the suction end pressure is gradually lowered. The pressure of the compressed air chamber between the fixed scroll and the orbiting scroll is lower than atmospheric pressure. The atmospheric pressure plus the spring pressure causes the winding between the orbiting scroll and the fixed scroll. The contact force is too large. Summary of the invention

SUMMARY OF THE INVENTION It is an object of the present invention to provide a scroll type volume displacement device capable of achieving an axial two-way directional movement, which has a double thrust bearing that orbits the orbiting scroll so that the orbiting scroll and the fixed When the pressure chamber between the scrolls changes, the thrust bearing can perform the corresponding two-way compliance movement to maintain the tightness of the pressure chamber behind the orbiting scroll, and the control between the orbiting scroll and the fixed scroll s contact.

A scroll type displacement device with a wraparound thrust bearing, comprising a main casing, a base casing, a rotating drive shaft, a fixed scroll and an orbiting scroll;

Wherein, there is a lower thrust bearing, a fixed bearing and an upper thrust bearing between the second end plate of the orbiting scroll and the base casing, and the lower thrust bearing forms a pressure chamber with the second end plate The upper thrust bearing is coupled to the lower thrust bearing, the fixed bearing is disposed on a bearing housing of the base housing, and the lower thrust bearing and the upper thrust bearing are similar to the orbiting scroll The orbiting movement.

Further, a pressure chamber is disposed between the rear end of the orbiting scroll and the upper thrust bearing, and after the pressure chamber introduces a pressure fluid, the orbiting scroll is pushed toward the fixed scroll .

Further, the upper thrust bearing and the lower thrust bearing are respectively adjacent to both end faces of the fixed bearing, and are fixed together, and the upper thrust bearing and the lower thrust bearing are driven by the fixed bearing The orbiting motion is made and the movement relative to the rotary drive shaft is made in the axial direction.

Further, the upper thrust bearing has a disc shape with a through hole therebetween, and the upper thrust bearing is uniformly distributed with three stepped holes and three threaded holes.

Further, the fixed bearing has a disc shape with a through hole therebetween, a stepped hole is concentrically disposed on a periphery of the through hole, and three countersunk screw holes and three holes are uniformly arranged around the fixed bearing. .

Further, the lower thrust bearing has a disc shape with a through hole therebetween, and the lower thrust bearing is provided with three countersunk screw holes and three holes.

The invention provides a scroll type volume displacement device with a bidirectional thrust bearing, which is provided with a double thrust bearing capable of orbiting along an orbiting wrap between the orbiting wrap and the base casing, and through the orbiting vortex The sealing contact between the coil and the thrust ball bearing seals the pressure chamber against the axial deflection force of the orbiting scroll; and is used to balance the possible sloshing in the orbiting motion of the orbiting scroll. DRAWINGS

Figure 1 is a longitudinal sectional view of a conventional scroll compressor having a single scroll one-way thrust bearing structure;

Figure 2 is a longitudinal sectional view of a scroll type displacement device with a two-way thrust bearing; Figure 3 is a schematic view of a rotary drive shaft of a scroll type displacement device with a two-way thrust bearing;

Figure 4 is a cross-sectional view showing a bidirectional thrust bearing mechanism of a scroll type displacement device with a two-way thrust bearing according to the present invention;

Figure 4A is a schematic view of the upper thrust bearing of the double-way thrust bearing mechanism of Figure 4;

Figure 4B is a schematic view of the fixed thrust bearing of the double-way thrust bearing mechanism of Figure 4;

Figure 4C is a schematic view of the lower thrust bearing of the double direction thrust bearing mechanism of Figure 4. detailed description

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A specific embodiment of a scroll type displacement device with a two-way thrust bearing according to the present invention will be described below with reference to the accompanying drawings. 2 is a longitudinal sectional view of a scroll type volume displacement device with a bidirectional thrust bearing, and FIG. 3 is a schematic view of a rotary drive shaft of a scroll type volume displacement device with a bidirectional thrust bearing, see FIG. As shown in FIG. 3, a scroll type displacement device with a bidirectional thrust bearing includes 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, and a scroll element 52 is fixed on the first end plate 51, 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. And maintain a phase angle displacement of 180° and a radial displacement equal to the orbital radius Ror. When the orbiting wrap 60 is orbitally moved relative to the fixed wrap 50, at least one sealed air chamber is formed between the wrap element 52 and the wrap element 62, and the first end plate 51 and the second end plate 61 are engaged with each other. The sliding between them changes the volume of the air chamber.

By making the orbiting scroll circularly (i.e., orbiting) relative to the fixed scroll, it is possible to cause line contact with the movement between the first end plate side wall and the second end plate side wall.

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 rear end of the fixed scroll 50 is fitted in the main casing 20, the base machine The casing 70 is coupled to the main casing 20, and the base casing 70 faces the rear end of the orbiting wrap 60.

A rotary drive shaft 40 includes a central shaft 41, a crankpin 42 and a crankpin 44. The crankpin 42 and the crankpin 44 are respectively disposed at one end of the central shaft 41, and the central shaft 41 extends through the intermediate portion of the base casing 70, and With the crank pin 42-end close to the rear end of the orbiting wrap 60, the crank pin 42 can drive the orbiting wrap 60 to a circular translation relative to the fixed wrap 50 through the crank pin bearing 260 of the central drive joint 64 (ie, The front and rear portions of the central shaft 41 are respectively supported by a bearing 33 and a bearing 34, and the bearing 33 and the bearing 34 are respectively disposed on the base casing 70 and supported by the base casing 70 such that the central shaft 41 is rotatably It is disposed in the base casing 70 while simultaneously positioning the center shaft 41 through the bearing 33 and the bearing 34. 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 35 to drive the motor 35. The lower central shaft 41 is rotatable about the axis S1-S1.

A bearing seat 63 is formed in a central portion of the second end plate 61. A crank pin bearing 260 is mounted in the bearing housing 63. The crank pin 42 is coupled to the crank pin bearing 260 via a central drive joint 64, and the crank pin 44 is driven by the drive bearing 65. The orbiting bearings 261 are coupled such that the central shaft 41 is coupled to the crank pin bearing 260 and the orbiting bearing 261, respectively. The motor 35 drives the central shaft 41 to rotate, drives the central drive joint 64 and the drive bearing 65, and drives the crank pin bearing 260 and the orbiting bearing 261. The crank pin bearing 260 drives the bearing housing 63 to move due to the bearing housing 63 and the orbiting scroll 60. The fixed connection enables the orbiting scroll 60 to be orbited relative to the fixed scroll 50 in accordance with the movement of the bearing housing 63.

An axial bore 43 is provided at one end of the central shaft 41 adjacent the crankpin bearing 260. The axial bore 43 is located adjacent the centerline S2-S2 of the crankpin 42 for axially or partially balancing the crankpin 42 and the crankpin. 44 The centrifugal force generated when the central shaft 41 rotates about the axis S1-S1.

There is an air inlet 80 on the main casing 20, and an intake passage 81 between the main casing 20 and the fixed scroll 50 and the orbiting scroll 60. When a working fluid such as air is passed through the main casing 20 The upper air inlet 80 enters the intake passage 81. A central air chamber 82 is disposed in a middle portion between the orbiting scroll 60 and the fixed scroll 50, and a pressure air chamber 83 is disposed between the rear end surface of the orbiting scroll 60 and the upper thrust bearing 72, and is located at the fixed scroll 50 and The pressure in the pressure plenum between the orbiting scrolls 60 can communicate with the pressure plenum 83 through the passages; the working fluid entering the suction passages 81 is drawn into the pressure formed between the fixed scrolls 50 and the orbiting scrolls 60. The air chamber is compressed in the orbiting motion of the orbiting scroll 60, then transmitted to the central air chamber 82, and finally discharged outward through the exhaust port 84 at the central portion of the first end plate 51 of the fixed scroll 50.

The mechanism (CSPS structure) having a centrally driven crankshaft-sliding joint and a peripheral crankpin-swinging connection mechanism in the present invention provides the axial and radial compliance motion of the orbiting scroll. The inventor's patent number is ZL200610121150. 3 is entitled "Improved scroll-type positive displacement compressor with full-floating floating scroll" Chinese patent. I will not repeat them here.

4 is a cross-sectional view of a bidirectional thrust bearing mechanism of a scroll type volume displacement device with a bidirectional thrust bearing according to the present invention, FIG. 4A is a schematic view of the upper thrust bearing of the bidirectional thrust bearing mechanism of FIG. 4, and FIG. 4B is a view of FIG. Schematic diagram of a fixed thrust bearing of a two-way thrust bearing mechanism, FIG. 4C is a schematic view of a lower thrust bearing of the two-way thrust bearing mechanism of FIG. 4, see FIG. 2, FIG. 4, FIG. 4A, FIG. 4B and FIG. It is shown that there is a lower thrust bearing 74, a fixed bearing 73 and an upper thrust bearing 72 between the second end plate 61 of the orbiting scroll 60 and the base casing 70. The upper thrust bearing 72 and the lower thrust bearing 74 are driven by the drive bearing 65 and the orbiting bearing 261 to make a similar wrap around the orbiting wrap 60.

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 fixed to the orbiting bearing 261, and the inner diameter of the orbiting 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 axis line S1-S1 of the crank pin 42 and the crank pin The distance of the axis S2-S2 of 44 is also equivalent to the orbiting radius of the orbiting scroll 60. When the crank pin 44 drives the drive bearing 65, the orbiting bearing 261 is driven, and finally the upper thrust bearing 72 and the lower thrust bearing 74 are orbited, while the orbiting bearing 261, the upper thrust bearing 72 and the lower thrust bearing 74 can be together. Do axial sliding. The spacer 75 installed in the hole 73d effectively prevents the upper thrust bearing 72 and the lower thrust bearing 74 from rotating.

There is 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. There is also a pressure plenum 83 through which the pressure plenum 83 is sealed from the surrounding area by a sealing element 90 and a sealing element 93. When the scroll device is activated, the elastic preload of the sealing member 90 and the sealing member 93 ensures that there is a slight axial contact between the two-phase engaged scrolls when the orbiting scroll 60 is urged toward the fixed scroll 50. In vacuum pump applications, the intake end is at atmospheric pressure and the exhaust end is at atmospheric pressure. The gas pressure in the pressure plenum 83 is higher than the atmospheric pressure, and a backward force (i.e., motor direction) axial force 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. At this time, under the action of the gas pressure in the pressure chamber 83, the upper thrust bearing 72 moves in the direction of the rear portion, that is, the motor, and is in sliding contact with the fixed bearing 73, and the latter receives the axial thrust.

When the scroll vacuum pump continues to operate, 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. At this time, the atmospheric pressure acting on the back surface of the upper thrust bearing 72 pushes the upper thrust bearing 72 and the lower thrust bearing 74 forward (fixed scroll direction), at which time the upper thrust bearing 72 and the lower thrust bearing 74 move forward, being The fixed bearing 73 is blocked, and the front surface of the lower thrust bearing 74 (toward the fixed scroll direction) is in sliding contact with the rear surface of the fixed bearing 73, and the latter receives the axial thrust to avoid the pressure difference between the atmospheric pressure and the vacuum. Causes an excessive axial force acting on the moving scroll.

The present invention provides an orbiting thrust bearing with a force that can withstand bidirectional axial forces. The thrust bearing may be a plain bearing, a rolling bearing, or a mixture of the two. The two-way thrust bearing enables the movable scroll to maintain the axial floating of the disturbing scroll and the axial direction of the fixed scroll when the axial force is greatly changed during the compression process or during the startup to the running process. Sealed contact.

Claims

Claim

A scroll type volume displacement device with a bidirectional thrust bearing, comprising a main housing (20), a base housing (70), a rotary drive shaft (40), a fixed scroll (50), and An orbiting scroll (60);

The utility model is characterized in that: a lower thrust bearing (74), a fixed bearing (73) and an upper thrust bearing are arranged between the second end plate (61) of the orbiting scroll (60) and the base casing (70). (72), the lower thrust bearing (74) and the second end plate (61) form a pressure plenum, and the upper thrust bearing (72) is coupled to the lower thrust bearing (74), the fixed bearing (73) disposed on a bearing housing of the base housing (70), the lower thrust bearing (74) and the upper thrust bearing (72) are similar to the orbiting scroll (60) motion.

2. The scroll type volume displacement device with a bidirectional thrust bearing according to claim 1, wherein: a rear end of said orbiting wrap (60) and said upper thrust bearing (72) have a The pressure plenum (83), after the pressure plenum (83) is introduced into the pressure fluid, the orbiting scroll (60) is pushed toward the fixed scroll (50).

The scroll type volume displacement device with a bidirectional thrust bearing according to claim 1, wherein: said upper thrust bearing (72) and said lower thrust bearing (74) are respectively adjacent to said fixed bearing (73) The two end faces are fixed together, and the upper thrust bearing (72) and the lower thrust bearing (74) are orbited by the fixed bearing (73), and are relatively axially opposed. Movement of the rotary drive shaft (40).

The scroll type displacement device with a bidirectional thrust bearing according to claim 3, wherein: said upper thrust bearing (72) has a disk shape with a through hole (72a) therebetween, said The upper thrust bearing (72) is uniformly surrounded by three stepped holes (72b) and three threaded holes (72c;).

The scroll type volume displacement device with a bidirectional thrust bearing according to claim 3, wherein: said fixed bearing (73) has a disk shape with a through hole (73a) in between The periphery of the through hole (73a) is concentrically provided with a stepped hole (73b), and the fixed bearing (73) is uniformly surrounded by three countersunk screw holes (73c) and three holes (73d).

The scroll type displacement device with a two-way thrust bearing according to claim 3, wherein: the lower thrust bearing (74) has a disc shape with a through hole (74a) therebetween, The lower thrust bearing (74) is uniformly surrounded by three countersunk screw holes (74b) and three holes (74c).