CN1152674A - Wedge-shaped crank axle for displacement vortex fluid compressor - Google Patents

Wedge-shaped crank axle for displacement vortex fluid compressor Download PDF

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Publication number
CN1152674A
CN1152674A CN 95121325 CN95121325A CN1152674A CN 1152674 A CN1152674 A CN 1152674A CN 95121325 CN95121325 CN 95121325 CN 95121325 A CN95121325 A CN 95121325A CN 1152674 A CN1152674 A CN 1152674A
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China
Prior art keywords
driving
mentioned
wedge
scroll member
crank pin
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Pending
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CN 95121325
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Chinese (zh)
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柯恩九
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Individual
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Individual
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Priority to CN 95121325 priority Critical patent/CN1152674A/en
Priority to PCT/CN1996/000103 priority patent/WO1997022808A1/en
Publication of CN1152674A publication Critical patent/CN1152674A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving

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

Abstract

The present invention relates to a wedge-shaped crankshaft of positive-displacement eddying fluid compression equipment. It is composed of a main shaft and a driving crankpin extended from tail end of said main shaft. The described driving crankpin has a driving face made in the form of wedge-shaped oblique plane, and the driving knuckle driven by said driving crankpin also has a wedge-shaped inclined driven face matched with the above-mentioned driving face, and the wedge-shaped driving face of the crankpin makes an included angle of less than 90 deg. with the movement direction of the moving volute element positioned in the compression equipment, so that it can make the driving force produce a radial component to overcome the radial separation force acting on the moving volute element and be directly proportional to the compressed fluid pressure so as to attain the goal of radial following.

Description

The Wedge-shaped crank axle of displacement vortex fluid compressor
The present invention is relevant with the displacement fluid device.More particularly, the present invention is relevant with the Wedge-shaped crank axle in the displacement vortex fluid compressor.
The technology of displacement vortex fluid compressor is well-known, and the U. S. Patent 802.182 of for example granting Creux has disclosed a kind of scroll-type apparatus.This device comprises two scroll members, and each scroll member has an end plate and a spiral scrollwork.These two scrollworks have identical geometrical shape, mesh each other and are kept at an angle and radial deflection, to cause many places line contact between their spiral curved surfaces.So, intermeshing scrollwork has formed at least one pair of air chamber that is sealed.Do the translation (here be referred to as revolution) of track for circle when a scrollwork with respect to another scrollwork, above-mentioned Line of contact just moves along spiral camber, thereby sealed air chamber's volume changes thereupon.The increase of volume or reduce to depend on the direction of relative movement between two scrollworks, like this, this device can be used for compression or expansion fluid.
General running principle below with reference to the traditional scroll compressor shown in Fig. 1 a-1d is done some explanations.Fig. 1 a-1d schematically shows intermeshing spiral scrollwork 1 and 2 and does relative movement with compressed fluid.Scrollwork 1 and 2 is meshing with each other and is being kept at an angle skew and radial deflection each other.Fig. 1 a has shown that the outer end of each scrollwork contacts with another scrollwork, and just sucting stage is just finished, and the A1 of sealed air chamber and the A2 of a pair of symmetry just form.
Fig. 1 b-1d has shown that successively crankshaft has rotated the position of scrollwork behind the several angle, and when crankshaft rotated, A1 of sealed air chamber and A2 were radially to move to the center of engagement scrollwork gradually with certain angle, and the volume of A1 and A2 progressively reduces simultaneously.When the angle of crankshaft when the state shown in Fig. 1 c arrives state shown in the 1d, A1 of sealed air chamber and A2 combine at center portion A place, when crankshaft continued to rotate, the air chamber after the above-mentioned merging further reduced its volume.When scrollwork was done relative, track for the translation of circle, the space outerpace shown in Fig. 1 b one 1d progressively changed to form new sealed air chamber, is wherein sealing compressed next fluid volumes (as the state shown in Fig. 1 c and the 1a).
Fig. 2 a and 2b grant the vertical drive face diameter shown in people's such as Caillat the U. S. Patent 4,767,293 to follower, and label 1 is a main shaft, and label 2 is the joint, and label 3 is the crank pin affixed with main shaft, and label 4 is the drive surface that crank pin drives the joint.This moment, the moving direction in joint 2 was directions Xs, and it is vertical in the common normal line direction of point of contact with two scrollwork helixes.The drive surface 4 of mechanism is vertical with the moving direction of moving scrollwork.This mechanism is in service, and the centrifugal force of parts such as moving scrollwork and joint need overcome the pressure of fluid in the air chamber, and scrollwork is tightly contacted with another scrollwork, reaches the purpose of sealing.Because all factors, inevitable error in the scrollwork manufacturing for example, and when sneak into foreign material and incompressible liquid in the air chamber, the joint is subjected to very big radial separation power when Separating force during greater than centrifugal force, is moved scrollwork and joint and is made a concession along the y direction.The radially follower that Here it is extensively adopts at present.
In some applications, automobile air conditioner compressor and use the air condition compressor of the variable speed of converter technique for example, compressor need be worked in bigger velocity variations scope.Especially in the automobile vortex air conditioner compressor was used, compressor will turn round in 800-6000 rev/min scope, thereby the centrifugal force of revolution scroll member changes greatly.Simultaneously, the operating conditions of car air conditioner, promptly the excursion of condensing temperature and evaporating temperature is also bigger, makes that radial separation power and driving force excursion are bigger.This situation give the revolution scroll member radially the design of follower brought difficulty.
Fig. 3 a and 3b are the fork schematic representation of apparatus of Japanese Saden company.Label 1 is a main shaft, and label 3 is for being fixed in the crank pin on the main shaft, and label 2 is the joint.O 1Be the gyration center of main shaft, O 2Be the geometrical center in joint, O 3Geometrical center for crank pin.If ignore inertial force and friction in this mechanism kinematic, the driving force F in its 3 pairs of joints 2 of crank pin will act on O 2And O 3Line on.This power can be decomposed into tangential driving force Ft and radial drive power Fr.The ratio of two power is definite value tg α.Because the crank pin center O of this structure 3To alignment of shafts O 1Distance (be O greater than second scrollwork revolution radius 2To O 1Distance).Therefore, the diameter of the main shaft of this structure is bigger, and the diameter in corresponding its joint is also bigger, can take a part of position of thrust-bearing like this, reduces the effective bearing area of thrust-bearing, all brings certain difficulty for design and manufacturing.
The Wedge-shaped crank axle that the purpose of this invention is to provide a displacement vortex fluid compressor, it can overcome the moving suffered fluid breakdown power radially of scrollwork, thereby provides one effectively radially to comply with mechanism.
In order to realize above-mentioned and other purpose, the invention provides a kind of Wedge-shaped crank axle of displacement vortex fluid compressor, wherein, described compression set mainly comprises:
Housing with fluid inlet and outlet;
One first scroll member, it is fixed in the housing, first scrollwork that has one first end plate and come out from its plane vertical extent;
One second scroll member, second scrollwork that it has one second end plate and comes out from its plane vertical extent; Above-mentioned two scrollworks are meshed each other, form sealed air chamber;
One crankshaft, it is made of a main shaft and a driving crank pin that stretches out from this main shaft tail end, described driving crank pin has a drive surface, and the drive surface that drives crank pin drives above-mentioned second scroll member by a driving bearing again by a driving joint and does the translation of track for circle with respect to above-mentioned first scroll member;
Wherein, the drive surface of above-mentioned driving crank pin is a wedge shape inclined-plane, and the face that is driven in above-mentioned driving joint is a wedge shape inclined-plane that cooperates with the drive surface that drives crank pin; The driving wedge surface that drives crank pin becomes one to be not equal to 90 angles of spending with the moving direction of above-mentioned second scrollwork.
In described device, above-mentioned second scroll member along above-mentioned driving crank pin drive wedge surface to the angle of the detaching motion direction of above-mentioned first scroll member and the moving direction of above-mentioned second scroll member between 45 degree are spent to 85.
Advantage of the present invention is, driving crank pin on the main shaft promotes the wedge shape inclined-plane in joint by a wedge shape inclined-plane, like this, the driving force that drives crank pin has a radial component, this radial component is passed to moving scroll member by the bearing that drives the joint, make scroll member can overcome the radial separation power of in the compressed fluid process, being born, reach and make between the dynamic and static scrollwork formed sealed air chamber in tangential sealing.
With reference to accompanying drawing reading detailed description hereinafter, the present invention will more easily be understood.
The scrollwork that Fig. 1 a-1d shows in the scroll compressor in the prior art is made the situation of track for the translation of circle;
Fig. 2 a-2b shows vertical drive face diameter in the prior art to follower;
Fig. 3 a-3b shows the fork drive unit in the prior art;
Fig. 4 shows the sectional drawing of displacement vortex compressor designed according to this invention;
The structural drawing that Fig. 5 a-5b shows the crankshaft with wedge shape drive surface designed according to this invention with and the stressing conditions analysis chart;
Fig. 6 a-6b shows the stressing conditions analysis chart and the longitudinal section thereof in driving joint designed according to this invention;
Fig. 7 shows the stressing conditions analysis chart between crankshaft and the driving joint.
Fig. 4 shows a Scrawl air condition compressor designed according to this invention.Compressor 10 comprises mainframe 20, compressor fore shell 21, the magnetic clutch 22 and first scroll member (or being called quiet scroll member) 60.Main radial bearing 32 is housed on the mainframe.Main shaft 40 is supported by main bearing 32 and the bearing 34 that is contained on the fore shell 21, and can rotate under the driving of magnetic clutch 22 around its axis S1.
One driving crank pin 42 is stretched out by the tail end of main shaft 40, and main shaft 40 and driving crank pin constitute so-called " crankshaft ".The central axis S1 of this driving crank pin central axis S2 and main shaft has a skew each other.This offset distance equals the revolution radius R or of second scroll member.So-called revolution radius is that second scroll member (or being scroll member) 50 is made the orbital radius of track for the translation of circle with respect to first scroll member 60.
First scroll member 60 has an end plate 61, the first scrollworks 62 from its plane vertical extent.First scroll member 60 is perpendicular and be fixed on the plane 64 of mainframe 20 with axis S1.Between the bottom of the end plate of the front end of the scrollwork of a scroll member and another scroll member, just kept appropriate gap like this.
This gap is must be enough big, even so that still can avoid contacting with each other between the bottom of the front end of a scrollwork and another end plate when tolerance being arranged and having thermal expansion to exist on making under normally moving.On the other hand, this gap again must be enough little, to guarantee that the forward end seal wearing piece 66 that radial leakage between compression air chamber can be positioned in the spiral chute of scrollwork front end is sealed.
Second scroll member 50 includes an end plate 51, the second scrollworks 52 from its plane vertical extent, and extends bearing support 53 from the end plate rear surface.
Scrollwork 52 and 62 intermeshes, and keeps the phase difference of 180 degree on angle, in the displacement that radially then keeps revolution radius R or.So, scrollwork 52 and 62 and end plate 51 and 61 between form a pair of sealed air chamber at least.Second scroll member 50 is connected with driving crank pin 42 with driving joint 41 by driving crankshaft bearing 43, and the effect of Oudan ring 45 is to prevent that second scroll member 50 from rotating.Under the driving of main shaft 40, second scroll member 50 is done orbiting with pressurized gas with revolution radius R or with respect to first scroll member 60.Working gas 91 enters by scroll member 50,60 formed induction chambers 95 through passage 93 from entering the mouth, and is compressed by scrollwork then, at last by exhaust port 70, discharges through outlet valve 71 and exhaust passage 72.
The crankshaft that Fig. 5 a-5b shows according to the present invention to be built, its driving crank pin 42 has the drive surface 140 that is the wedge shape inclined-plane, main shaft 40 in the running, drive surface 140 promotes to drive the face that is driven 142 (Fig. 6 a-6b) in joint 41, and the face that is driven 142 that drives joint 41 also is the wedge shape inclined-plane that matches with the drive surface 140 that drives crank pin 42.As shown in Figure 7, the crank pin 42 affixed with main shaft 40 drives joint 41, drives moving scrollwork and does the translation of track for circle.Drive surface with make the moving direction (illustrated directions X) of moving scrollwork of track this moment and become one less than the 90 angle α that spend for the translation of circle.It is pointed out that exactly the moving direction in joint is vertical with the common normal line of two spiral type line point of contact, just two lines of centres with main shaft and joint are vertical.Therefore, when the joint when the drive surface direction moves (promptly producing servo-actuated), angle α changes.But this servo-actuated is small, so this angle can be thought certain value.We claim that angle α is the key groove of Wedge-shaped crank axle the back.Wedge-shaped crank axle and interarticular surface of contact should be smooth, and good lubricating arranged.Therefore, crankshaft can only be within F1 and the scope between the F2 shown in Figure 7 to the driving force in joint.F1 is vertical with drive surface with the angle separated time that F2 forms the angle, and its angle is 2 Φ.Φ is the friction angle of surface of contact, and as shown in the figure, a part of driving force is converted into radial thrust, makes the moving suffered radial thrust of scrollwork be directly proportional with radial separation power, to reach the purpose of good radially follower structure.The locking angle of Wedge-shaped crank axle should be considered two states when design: first state is that when compression set normally moved, second scrollwork should radially be close to first scrollwork, to form the air chamber of sealing.At this moment, because the effect of frictional force, crankshaft is F2 to the driving force that drives the joint.Therefore have:
Tg (α+Φ)=Ft/Fr 2(1) (see figure 7)
Fr 2＞Fs-Fc (2) wherein Φ is 41 friction angle of driving crank pin 42 and driving joint, Fs is cold media air imposes on second scroll member in the process of being compressed a radial separation power, and Fc is second scroll member and drives the centrifugal force that the joint is produced in revolution.Second state is to have sneaked into some foreign material in the foozle of spiral type line or the air chamber, when second scroll member can not need to make a concession by theoretical track operation.At this moment, crankshaft is the F1 (see figure 7) to the driving force that drives the joint.Therefore have:
tg(α－Φ)＝Ft/Fr (3)
Fr＜=Fs-Fc+Fd (4) wherein Fd is the pressure maximum that two scrollwork sidewalls can stand.Comprehensive above four formulas can obtain the design principle of crankshaft locking angle:
arctg(Ft/(Fs－Fc＋Fd))＋Φ＜＝
α＜=arctg (Ft/ (Fs-Fc))-Φ (5) is when (5) when formula is met, and the radial seal and the safety that just can reach between two scrollworks are made a concession.
In addition, equal the revolution radius of second scrollwork from driving crank pin 42 geometrical centers of the present invention to the distance at main shaft 40 centers, so its compact structure, can dwindle the volume of drive unit.Thereby increase the effective bearing area of thrust-bearing.
Described above, though be preferred embodiment of the present invention, skilled person in the art can make in view of the above belong in the scope of the invention to structure, layout, the change of part or variation.The present invention is limited by appending claims.The claimed scope of claims will comprise and the cutting device of claim in meaning or structure equivalent.

Claims (2)

1. the Wedge-shaped crank axle of a displacement vortex fluid compressor, wherein, described compression set mainly comprises:
Housing with fluid inlet and outlet;
One first scroll member, it is fixed in the housing, first scrollwork that has one first end plate and come out from its plane vertical extent;
One second scroll member, second scrollwork that it has one second end plate and comes out from its plane vertical extent; Above-mentioned two scrollworks are meshed each other, form sealed air chamber;
One crankshaft, it is made of a main shaft and a driving crank pin that stretches out from this main shaft tail end, described driving crank pin has a drive surface, and the drive surface that drives crank pin drives above-mentioned second scroll member by a driving bearing again by a driving joint and does the translation of track for circle with respect to above-mentioned first scroll member;
It is characterized in that the drive surface of above-mentioned driving crank pin is a wedge shape inclined-plane, the face that is driven in above-mentioned driving joint is a wedge shape inclined-plane that cooperates with the drive surface that drives crank pin; The driving wedge surface that drives crank pin becomes one to be not equal to 90 angles of spending with the moving direction of above-mentioned second scrollwork.
2. device as claimed in claim 1 is characterized in that, above-mentioned second scroll member along above-mentioned driving crank pin drive wedge surface to the angle of the detaching motion direction of above-mentioned first scroll member and the moving direction of above-mentioned second scroll member between 45 degree are spent to 85.
CN 95121325 1995-12-18 1995-12-18 Wedge-shaped crank axle for displacement vortex fluid compressor Pending CN1152674A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN 95121325 CN1152674A (en) 1995-12-18 1995-12-18 Wedge-shaped crank axle for displacement vortex fluid compressor
PCT/CN1996/000103 WO1997022808A1 (en) 1995-12-18 1996-11-15 A wedge crank shaft for scroll-type fluid displacement compression apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 95121325 CN1152674A (en) 1995-12-18 1995-12-18 Wedge-shaped crank axle for displacement vortex fluid compressor

Publications (1)

Publication Number Publication Date
CN1152674A true CN1152674A (en) 1997-06-25

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Application Number Title Priority Date Filing Date
CN 95121325 Pending CN1152674A (en) 1995-12-18 1995-12-18 Wedge-shaped crank axle for displacement vortex fluid compressor

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WO (1) WO1997022808A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107255076A (en) * 2017-06-08 2017-10-17 中国石油大学(华东) A kind of radial direction covariant mechanism of screw compressor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19910460A1 (en) 1999-03-10 2000-09-21 Bitzer Kuehlmaschinenbau Gmbh compressor
DE19910458C2 (en) * 1999-03-10 2003-01-09 Bitzer Kuehlmaschinenbau Gmbh compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2737584B2 (en) * 1991-12-27 1998-04-08 三菱電機株式会社 Scroll compressor
JP2894390B2 (en) * 1992-01-10 1999-05-24 三菱電機株式会社 Scroll compressor
JP3106737B2 (en) * 1992-11-17 2000-11-06 株式会社豊田自動織機製作所 Scroll compressor
JP3337831B2 (en) * 1993-10-21 2002-10-28 株式会社日本自動車部品総合研究所 Scroll compressor
JPH07324689A (en) * 1994-05-31 1995-12-12 Mitsubishi Heavy Ind Ltd Scroll type fluid compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107255076A (en) * 2017-06-08 2017-10-17 中国石油大学(华东) A kind of radial direction covariant mechanism of screw compressor
CN107255076B (en) * 2017-06-08 2019-05-31 中国石油大学(华东) A kind of radial covariant mechanism of screw compressor

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