CN1011611B - Refrigerant compressor - Google Patents
Refrigerant compressorInfo
- Publication number
- CN1011611B CN1011611B CN 88100840 CN88100840A CN1011611B CN 1011611 B CN1011611 B CN 1011611B CN 88100840 CN88100840 CN 88100840 CN 88100840 A CN88100840 A CN 88100840A CN 1011611 B CN1011611 B CN 1011611B
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- China
- Prior art keywords
- mentioned
- radial bearing
- transmission shaft
- compressor
- wobble plate
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Abstract
The present invention relates to a swing-disk type compressor which has the technical scheme that a casing is provided with a plurality of air cylinders and a crank chamber adjacent to the air cylinders; each air cylinder is provided with a reciprocating piston sliding in the air cylinder; a drive mechanism is connected with the pistons, and a reciprocating action is obtained; the drive mechanism is provided with a transmission shaft which penetrates through a radial bearing and a wedge-shaped cam rotor, and the transmission shaft is supported on the casing of the compressor to rotate; the axial end surface of the rotor and the axial end surface at least corresponding to the upper end part are inclined at an angle. Thus, the axial end surface of the rotor uniformly comes into contact with a thrust bearing, and the damage to the thrust bearing is prevented.
Description
The present invention is relevant with the refrigeration compressor that is used for automotive air-conditioning system, the concrete relevant wobble plate compressor that improved transmission shaft cantilevered support structure is arranged.
The wobble plate compressor that the transmission shaft cantilevered support structure is arranged is known.These structures are at U. S. Patent the 3rd, 552, No. 886 and 3,712, disclose in No. 759.
Referring to Fig. 1, a kind of wobble plate compressor 1 that traditional cantilever structure is arranged has 2, one front end-plates 3 of a columnar compression case and the end plate that form is a cylinder cap 4.A cylinder body 21 and a crank chamber 22 are arranged in the compression case 2.Front end-plate 3 is fixed on the end face of compression case 2, is placed on the cylinder cap 4 of compression case 2 other ends, is fixed on 21 1 end faces of cylinder body with the bolt 41 that passes valve plate 5.Middle part at front end-plate 3 forms a hole 31, and transmission shaft 6 passes therethrough.
Be provided with the annular balance 10 of angular wheel 101 at the middle part, by a needle roller thrust bearing 16, be placed on the ramp surface 81 of wedge cam rotor 8, balance is supported in through a spherical parts 12 on the terminal of supporting member 11 and does pitching movement, between cylinder body 21 and supporting member 11, insert a key, prevent the supporting member rotation.Supporting member 11 is placed in the center hole 211 of cylinder body 21 middle parts formation, and it has an angular wheel 111 and the shank 112 that hollow portion 113 is arranged.On the end in adjusting screw 17 centre holes 211.A helical spring 13 is placed in the hollow portion 113 of shank 112, pushes supporting member 11 to balance 10, and the angular wheel 101 of the angular wheel 111 engagement balances 10 of supporting member 11 prevents balance 10 rotations.
Some cylinders 212 isogonism ground on cylinder body 21 distributes, and has piston 14 to slide in each cylinder 212.Each piston 14 is connected with the circumference of balance 10 by each connecting rod 15: an end of connecting rod 15 is connected with piston 14 with ball-joint, and the other end is connected with balance 10 with ball-joint.
Cylinder head 4 has a discharge side 42 and a suction chamber 43 of surrounding discharge side 42.Have a suction bole 51 to pass from valve plate 5, suction chamber 43 and cylinder 212 are communicated, a tap hole 52 passes from valve plate 5, and cylinder 212 and discharge side 42 are communicated.
During running, when transmission shaft 6 was driven by the magnetic clutch on the tubular extension part 35 that is installed in front end-plate 3 18 by power source, cam follower 8 was with transmission shaft 6 rotations, thereby balance 10 is not done pitching movement with cam follower 8 rotations.Therefore, each piston 14 is owing to the pitching movement of balance 10, and work is back and forth movable in cylinder 212.The bounce-back intensity of helical spring 13 can be regulated by the stubborn joint screw 17 that tunes.Therefore, thrust-bearing 9, cam follower 8, balance 10, angular wheel 101, even the corresponding axial clearance between steel ball 12 and the supporting member 11 etc. is the dimensional changes that has temperature variation to cause, with the size error of processing, also can the gap be maintained fixed by the bounce-back intensity of adjusting color screw spring 13.
Generally as the refrigeration compressor of air conditioning equipment of car, therefore, under general service condition, compressor requires to have enough serviceabilities to the compressor of above-mentioned swing-plate type.But under severe condition, for example under high temperature condition during long-duration driving, transmission part might be stung tightly (seizure), thereby compressor can not keep enough serviceabilities.
To stinging at the compressor transmission part that has really damaged under this condition after tight reason performs an analysis, find that the outer surface of the transmission shaft 6 that contacts with the internal surface of (supporting drive shaft 6) radial needle bearing 7 has taken place cracked.Fragment on the transmission shaft 6 damages transmission part, and compressor is just stung tight phenomenon.
Referring to Fig. 2, the contact surface of its expression transmission shaft 6 and radial needle bearing 7.Crackedly in regional A, take place.The glossy surface on expression transmission shaft 6 and radial bearing 7 actual contact surfaces is an area B.According to the top fact, can see that the outer surface of transmission shaft 6 contacts with the internal surface of radial bearing 7 is inhomogeneous, promptly transmission shaft 6 may partly contact with radial bearing 7.
Referring to Fig. 3, the relation of the power between its each parts of expression compressor.The reason of part contact can be done following analysis.Act on the axial force on the cam follower 8, comprise total gas pressure and end thrust F2 that each piston 14 compresses, F2 is the bounce-back intensity of helical spring 13.Total gas pressure F1 is on the some A of cam follower 8 when piston 14 is on upper dead center, and some A is near connecting rod 15 ball-joints.End thrust F2 acts on the center portion of cam follower 8.Because on the inclined surface 81 that above-mentioned total gas pressure F1 and end thrust F2 act on cam follower 8, radially producing radial component F3 and F4.
Produce on thrust-bearing 9 with total gas pressure F1 and the opposite axial reaction force F5 of end thrust F2 direction, so the equilibrium of forces axially.But component F3 and F4 are not had equilibrant, thereby produce moment, with the some B rotation of cam follower 8 around thrust-bearing 9, so cam follower 8 just separates with thrust-bearing 9 on lower dead centre in a side relative with upper dead center.Therefore, transmission shaft 6 is from the axis tilt of radial bearing 7, and at C point and D point place, transmission shaft 6 partly contacts with radial bearing 7.The inclination angle [theta] of the axis of transmission shaft 6 and radial bearing 7 is decided by the axial length of radial bearing 7 and the gap between radial bearing 7 internal surfaces and transmission shaft 6 outer surfaces.
In above-mentioned structure, the reaction force F6 and the F7 of radial bearing 7 act on the transmission shaft 6, and equilibrium of forces can be represented by the formula:
F3+F4＝F6-F7
Be decided to be 11-14 as each size, r1 or r2, as shown in Figure 3, just moment as shown in the formula:
F3·11+F4·12+F6·13-F1（r2-r1）-F2·r2-F7·14＝0
As mentioned above, suppose that transmission shaft 6 partly contacts radial bearing 7 when driving, and can produce cracked betwixt.Having under the condition of inclination angle [theta], total change with gas pressure F1 from the axial reaction force F6 and the F7 of radial bearing 7 to transmission shaft 6 effects.When having common gap, inclination angle [theta] is predefined in zero to 0.04 degree scope.Therefore, cracked being easy to taken place under severe condition, for example will produce under high air conditioning load.
Main purpose of the present invention is to propose a kind of wobble plate compressor, even when using compressor under severe condition, can obtain enough serviceabilities.
Another object of the present invention is to propose a kind of wobble plate compressor, under high air-conditioning loading condiction, can prevent that transmission shaft from contacting with part between radial bearing.
Wobble plate compressor of the present invention has a compression case, and near a crank chamber of some cylinders and cylinder is wherein arranged.Place a piston that reciprocatingly slides in each cylinder.A driving mechanism is connected with piston, obtains reciprocating action.Driving mechanism has a transmission shaft, is bearing on the compression case by radial bearing and wedge cam rotor and rotates.The axial end of cam follower is being certain angle that tilts in the axial end scope of upper end portion at least, and therefore, the axial end of cam follower guarantees and the thrust-bearing even contact.
Other purposes of the present invention, by the following narration with reference to accompanying drawing about the desirable embodiment of the present invention, just can have gained some understanding in characteristics and other aspects.
Fig. 1 analyses and observe for traditional wobble plate compressor.
Fig. 2 is the local unfolded drawing of transmission shaft outer surface among Fig. 1.
Fig. 3 is the cam follower of illustration in Fig. 1 and the key diagram of the relation of the power on the transmission shaft.
Fig. 4 is wobble plate compressor one embodiment of the present invention, and analysing and observe of its part illustrates the state of cam follower and transmission shaft assembly parts.
Fig. 5 analyses and observe the state of front end-plate and transmission shaft assembly parts in the presentation graphs 4 for a compressor part.
Fig. 6 analyses and observe for the amplification of an assembly parts part among Fig. 5, has external force to act in the above.
Fig. 7 is the analysing and observe of a compressor part, and expression has the end plate shown in Figure 5 that another external force acts on and the state of transmission shaft assembly parts in the above.
Fig. 8 analyses and observe for the amplification of an assembly parts part shown in Figure 7.
Fig. 9 (a) analyses and observe for radial bearing in another embodiment of the present invention.
Fig. 9 (b) analyses and observe presentation graphs 9(a for a compressor part) state of radial bearing assembly parts.
Figure 10 (a) analyses and observe for the radial bearing of another embodiment of the present invention.
Figure 10 (b) analyses and observe presentation graphs 10(a for a compressor part) in the state of radial bearing assembly parts.
Figure 11 is the analysing and observe of a compressor part, and expression has the state of the assembly parts of front end-plate of the radial bearing shown in Fig. 9 (a) and transmission shaft shown in Figure 4, has an end thrust to act on the transmission shaft.
Figure 12 is the analysing and observe an of part of compressor, and expression has the state of assembly parts among Figure 11 that external force acts in the above.
Referring to Fig. 4, the transmission shaft of expression one embodiment of the invention and the structure of a wedge cam rotor.Cam follower 8 has wedge shape section, and an axial end of cam follower 8 is delimited with straight line, as the line St among the figure.The axis of transmission shaft 6 represents with line OR that in Fig. 4 axle 6 and the traditional mode of cam follower 8 usefulness are assembled, and the line St that the axis of axle and the axial end of cam follower 8 constitute is vertical.The present invention in contrast, transmission shaft 6 is assembled on the cam follower 8, the axes O S of transmission shaft 6 is tilted and axes O R forms a certain angle (Fig. 4 represents θ 1 degree), thereby stretches to the upper dead center side, just upper dead center depends on a thicker side of cam follower 8.Its numerical value can be obtained with following formula:
θ1≥tan
-1（c/l）
1 is the axial length of radial bearing 7 in the formula, and c is the gap between radial bearing 1 internal surface and transmission shaft 6 outer surfaces.In addition, be placed on the plate 91 of the radial needle bearing 9 on the axial end of cam follower 8,, form angle θ 2 in tilting of cam follower 8 than the thickness portion place.Angle θ 2 is predetermined, so if θ 1 is tan
-1(c/l), deduct the value of θ 2 greater than θ 2 from θ 1.
Referring to Fig. 5, the assembly parts of cam follower 8 and transmission shaft 6.Drive shaft cartridge is on wobble plate compressor 1 front end-plate 3.In this case, end thrust F2 acts on the end face of transmission shaft 6.Because end thrust F2 is greater than the intensity of cam follower 8 and transmission shaft 6 joints,, be to get in the position of the line OR ' of φ thereby the axes O R of cam follower 8 moves to angle so the thin part of cam follower 8 is pushed to the interior edge face of front end-plate 3.At this moment, the angle between the axes O R ' of the axes O B of radial bearing 7 and cam follower 8 becomes θ 2, and it is identical with the inclination angle of the thick portion of the cam follower 8 shown in Fig. 6.As mentioned above, the angle between the axes O B of the axes O S of transmission shaft 6 and radial bearing 7 is θ, and it is by tan
-1(c/l) determine.Just, transmission shaft 6 is from transmission shaft shown in Figure 46 positions, the angle of turning left φ.Therefore, if the strength coefficient of the joint of cam follower 8 and transmission shaft 6 is k, just there is the torque M s to the right that equals k φ on transmission shaft 6, to act on.
In above-mentioned situation, act on the power on the above-mentioned part and the balance of moment, can be represented by the formula:
F4+F6＝F7
F2＝F5
F5R+F612-F411-F7（12+13）＝0
Ms＝kφ＝F7（12+13）-F612
In the formula 11,12,13, R is respectively the size shown in Fig. 5, F2, and F4, F5, F6, or F7 is the power on the said structure that acts among Fig. 5; F4 is to serve as the component that the basis produces with end thrust F2, and F5 is the reaction force of thrust-bearing 9, and F6 is the reaction force of radial bearing 7, and F7 is the reaction force of radial bearing 7.
As shown in Figure 7, when compressor 1 running, comprise the external force of total gas pressure F1 and end thrust F2, act on the inclined surface 81 of cam follower 8.Radial component F3 and F4 produce according to external force F1 and F2, act on the inclined surface 81 of cam follower 8.These radial components F3, F4 presses cam follower 8 to the upper dead center thruster.Therefore, transmission shaft 6 is around the some M shown in Fig. 5, turn left, point M is in the outer end of radial bearing 7, be exactly that transmission shaft 6 relies on the place of cam follower 8 to the lower dead centre side shifting, it is parallel that thereby the axes O S of the axes O B of radial bearing 7 and transmission shaft 6 becomes, so the outer surface of transmission shaft 6 is by the upper inside surface support of radial bearing 7.
Angle between the axial end of the axes O S of transmission shaft 6 and cam follower 8 from Fig. 7 to Fig. 4 and 5, changes the φ degree, and promptly θ 1 subtracts θ 2 degree.If the strength coefficient of the attachment portion of cam follower 8 and transmission shaft 6 is k, torque to the right is Ms, and Ms equals k φ, and effect on transmission shaft 6 is just transmission shaft 6 can guarantee to make even contact with the upper inside surface of radial bearing 7.
Under above-mentioned situation, act on power on above-mentioned each parts and the balance between the torque, can be represented by the formula:
F3+F4＝F6
F1+F2＝F5
F5R-F411-F1R′-F6（12+14）＝0
Ms＝kφ＝F6（12+14）
In the formula 11,12,13, R or R ' are the size shown in Fig. 6, F1, F2, F3 or F4 are power same as described above, and F5 is the reaction force of thrust-bearing 9, and F6 is the reaction force of radial bearing 7, Ms is owing to the angle that changes between transmission shaft 6 and the cam follower 8, the torque to the right of effect on transmission shaft 6.The angle φ that changes is that angle θ 1 deducts angle θ 2.
As indicated above, when compressor 1 running, the interior circumferential portion of the outer surface of transmission shaft 6 and radial bearing 7 guarantees even contact, thereby prevents transmission shaft 6 tearing surface portions.And, as shown in Figure 8, angle θ 2 is arranged at the axial end than thrust seat ring 91 on the thickness portion and cam follower 8 of cam follower 8.So thrust seat ring 91 and thrust-bearing 9 even contact.So also can prevent the 91 surface portion tearing of thrust seat ring.
Referring to Fig. 9 (a), the expression wobble plate compressor is used, can improve the structure of the radial bearing of compressor durability.Some needle rollers 302 that radial bearing 30 has a cylindrical shape seat ring 301 and isogonism is placed on the perimeter surface in seat ring 301.Seat ring in uneven thickness, promptly radially an end of seat ring 301 is thicker, and the other end is thinner.Therefore the internal surface of seat ring 301 is tapered, and the shape of tapered collar is just arranged.Radial bearing 30 is suppressed the hole 31 of front end-plate into from crank chamber side, make thrust seat ring 301 than its position of thickness portion contact stop ring 32(shown in Fig. 9 (b)).After radial bearing 30 assemblings, the internal surface of radial bearing 30 becomes the surface of tapered collar, and the large diameter of radial bearing 30 is in crank chamber side.Angle between the axes O B of radial bearing 30 and the tapered collar surfaces A C is predefined for θ 3 degree.
The above-mentioned final structure of the radial bearing that assembling finishes can be finished with common bearing.Just as shown in Figure 8, there is taper shape in the hole 33 of front end-plate 3, reduces gradually towards the outside internal diameter of compressor.With the general bearing 34 of structure shown in Figure 10 (a), suppress in the cone shape hole 33, in the one end face patchhole 33, against stop ring 32, shown in Figure 10 (b).Therefore, the internal surface of radial bearing 34 becomes conical ring.Angle between the axes O B of radial bearing 34 and the tapered collar surfaces A C is predefined for θ 3 degree.
If the needle roller 302 of each radial bearing 30 and 34 and 342 axial length are l, the gap between the minimum diameter of transmission shaft 6 outer surfaces and each radial bearing 30 and 34 is c, and then angle θ 1 can be represented by the formula:
θ1≥tan
-1（ (c+1·tanθ3)/1 ）
In the formula as tan
-1(c+ltan θ 3) represents that with θ 4 then θ 1 is more preferably greater than θ 4.
Referring to Figure 11, expression transmission shaft, the package assembly of front end-plate and cam follower.30 supportings of transmission shaft 6 usefulness radial bearings, end thrust F2 is with cam follower 8 axial push.The end thrust F2 available adjustment screw 17 that comprises helical spring 13 bounce-back intensity is regulated, thus the axial end of cam follower 8 can with thrust-bearing 9 even contact.Because end thrust F2 acts on the ramp surface 81 of cam follower 8, the lower dead centre side of cam follower 8 is also by backup thrust-bearing 9, so the axes O R of cam follower 8 moves, and reaches on the line OR ', and the angular distance of angle φ is arranged between line OR ' and axes O R.Line OR ' is parallel with the axes O B of radial bearing 30, becomes 4 jiaos of θ with the axes O s of transmission shaft 6.Angle θ 4 is decided by tan
-1((c+ltan θ 3)/(l)) transmission shaft 6 remains in the angular distance of an angle φ of transmission shaft 6 positions.
If the strength coefficient of the attachment portion between transmission shaft 6 and the cam follower 8 is k, it is that the dextrad torque Ms of k φ acts on transmission shaft 6 that numerical value is then arranged.The balance of any power and torque M s is represented with following formula:
F4+F6＝F7
F2＝F5
F5R+F612-F411-F7（12+13）＝0
Ms＝kφ＝F7（12+13）-F612
In the formula 11,12,13 or R be the size of each several part, F2, F4, F5, F6 or F7 are the power on the each several part among Fig. 9 that acts on,
F4: the radial force F2(of effect such as the inclination angle on inclined-plane 81 are α on cam follower 8 inclined surfaces 81, and then F4 represents with this formula: F4=F2tan α)
F5: be the reaction force of thrust-bearing 9
F6: be the reaction force of radial bearing 30
F7: be the reaction force of radial bearing 30
Referring to Figure 12, during running, act on the some A of the inclined surface 81 upper dead center sides of cam follower 8 as total gas pressure F1, at this moment owing to transmission shaft 6 contacts with the internal surface of radial bearing 30 is eccentric on the some N of outer end, so transmission shaft 6 centers on some N to the upper dead center sideway swivel, thereby with the internal surface of radial bearing 30, in upper dead center side even contact, as shown in figure 12.Just transmission shaft 6 is from its origin-location shown in Figure 11, to upper dead center sideway swivel angle θ 3+ θ 4.Therefore, the upside on the annular cones surface of the axes O s of transmission shaft 6 and radial bearing 30 is parallel.
As mentioned above, since cam follower 8, thrust-bearing 9, balance 10, angular wheel 101 does not have axial clearance between steel ball 12 and the angular wheel 111 etc., so end thrust F2 becomes F8, comprise the power that separate with front end-plate 3 interior edge faces the underpart that prevents cam follower 8 among the F8.Component F4 becomes F9 again.When internal surface even contact at upper dead center side and radial bearing 30 of the outer surface of transmission shaft 6, the balance between any power and the dextrad torque can be represented by the formula:
F3+F9＝F6
F1+F8＝F5
F5R-F911-F1R′-F6（12+14）＝0
Ms＝k（φ+θR）＝F6（12+14）
θR＝θ3+θ4
In the formula 11,12,13, R or R ' are the size of each several part, F1, F3, F8 or F9 are the power on the each several part among Figure 12 that acts on, and F5 is the reaction force of thrust-bearing 9, and F6 is the reaction force of radial bearing 30, Ms is the dextrad torque that changes effect on transmission shaft 6 according to the angle of transmission shaft 6 and cam follower 8 in (φ+θ 3+ θ 4) scope, and θ R is the angle between transmission shaft 6 axes O s shown in Figure 11 and the radial bearing 30 internal surface upsides.
If during compressor operation, end thrust F2 is less than a predetermined power, and discord thrust-bearing 9 contacts of the underpart of cam follower 8 just can form a certain angle in the upper dead center side by the axial end with cam follower 8, just can uniform the contact be arranged with thrust-bearing 9.
Though the present invention's associated ideal embodiment is described in detail, only do for example, the present invention not with this as restriction.Be familiar with this skill field person's easy to understand, within the scope of the invention, also can do other variation and modification.
Claims (11)
1, a kind of wobble plate compressor, a compression case is arranged, some cylinders and a crank chamber adjacent with this cylinder are wherein arranged, there is a reciprocating piston to slide in each cylinder inside, front end-plate with center hole is installed on the end surfaces of above-mentioned compressor shell, a driving mechanism is connected with above-mentioned piston, piston is moved back and forth in above-mentioned cylinder, above-mentioned driving mechanism comprises that being rotatably supported in transmission shaft and in the above-mentioned front end-plate center hole by a radial bearing has axial end and be connected to wedge cam rotor on the above-mentioned transmission shaft, it is characterized in that the axial end of upper end of above-mentioned wedge cam rotor and the axial end of above-mentioned wedge cam rotor have a predetermined inclination angle [theta] 2, wherein θ 2 is greater than 0 °, be less than or equal to θ 1, wherein θ 1 is more than or equal to tan
-1(c/1), C is the gap between the outer surface of the internal surface of above-mentioned radial bearing and the above-mentioned transmission shaft on above-mentioned radial bearing one end in the formula, the 1st, and the axial length of above-mentioned radial bearing.
2, wobble plate compressor as claimed in claim 1 is characterized in that above-mentioned at least one upper end portion axial end is the surface on the thick upper end portion of above-mentioned cam follower.
3, wobble plate compressor as claimed in claim 2 is characterized in that above-mentioned radial bearing comprises the cylindricality seat ring with an internal surface and some needle rollers that equally spaced are placed in one, and the internal surface of above-mentioned seat ring is taper, and has conical inner surface.
4, wobble plate compressor as claimed in claim 2 is characterized in that the front end center hole of above-mentioned end plate comprises the internal surface with conical surface, and above-mentioned radial bearing is placed in this internal surface.
5, wobble plate compressor as claimed in claim 2 is characterized in that above-mentioned transmission shaft tiltedly is connected on the above-mentioned cam follower to be θ 1 angle lapping with axial end.
6, wobble plate compressor as claimed in claim 5, it is characterized in that above-mentioned radial bearing has cone-shaped inner surface, its radial thickness reduces on the direction of above-mentioned front end-plate gradually in the inboard from compression case, with the θ 3 at an angle of shape between the longitudinal axis of the above-mentioned internal surface of above-mentioned radial bearing and above-mentioned bearing, wherein θ 3 is less than or equal to θ 1.
7, wobble plate compressor as claimed in claim 6, it is characterized in that θ 1 be restricted to more than or equal to
tan
-1（ (c+1·tan03)/1 ）
8, wobble plate compressor as claimed in claim 2, it is characterized in that above-mentioned radial bearing has cone-shaped inner surface, its radial thickness reduces on the direction of above-mentioned front end-plate gradually in the inboard from compression case, with the θ 3 at an angle of shape between the longitudinal axis of the above-mentioned internal surface of above-mentioned radial bearing and above-mentioned bearing, wherein θ 3 is less than or equal to θ 1.
9, wobble plate compressor as claimed in claim 5, it is characterized in that θ 1 be restricted to more than or equal to
tan
-1（ (c+1·tanθ3)/1 ）
10, wobble plate compressor as claimed in claim 8, it is characterized in that θ 1 be restricted to more than or equal to
tan
-1（ (c+1·tanθ3)/1 ）
11, a kind of wobble plate compressor, a compression case is arranged, some cylinders and a crank chamber adjacent with this cylinder are wherein arranged, there is a reciprocating piston to slide in each cylinder inside, front end-plate with center hole is installed on the end surfaces of above-mentioned compressor shell, a driving mechanism is connected with above-mentioned piston, piston is moved back and forth in above-mentioned cylinder, above-mentioned driving mechanism comprises that being rotatably supported in transmission shaft and in the above-mentioned front end-plate center hole by a radial bearing has axial end and be connected to wedge cam rotor on the above-mentioned transmission shaft, it is characterized in that the upper end portion axial end of above-mentioned wedge cam rotor angle of axial end inclination with respect to above-mentioned wedge shape rotor, this angle is greater than θ, less than tan
-1(c/1), wherein c is the gap between the outer surface of the internal surface of above-mentioned radial bearing before external force adds the time and the rotatingshaft on above-mentioned radial bearing one end, the 1st, the axial length of above-mentioned radial bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88100840 CN1011611B (en) | 1988-02-11 | 1988-02-11 | Refrigerant compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88100840 CN1011611B (en) | 1988-02-11 | 1988-02-11 | Refrigerant compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1035164A CN1035164A (en) | 1989-08-30 |
| CN1011611B true CN1011611B (en) | 1991-02-13 |
Family
ID=4831526
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 88100840 Expired CN1011611B (en) | 1988-02-11 | 1988-02-11 | Refrigerant compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1011611B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009064760A1 (en) * | 2007-11-12 | 2009-05-22 | David Baker | Vapor compression and expansion air conditioner |
-
1988
- 1988-02-11 CN CN 88100840 patent/CN1011611B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| CN1035164A (en) | 1989-08-30 |
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