CN102341599A - Swash plate compressor - Google Patents
Swash plate compressor Download PDFInfo
- Publication number
- CN102341599A CN102341599A CN2010800104509A CN201080010450A CN102341599A CN 102341599 A CN102341599 A CN 102341599A CN 2010800104509 A CN2010800104509 A CN 2010800104509A CN 201080010450 A CN201080010450 A CN 201080010450A CN 102341599 A CN102341599 A CN 102341599A
- Authority
- CN
- China
- Prior art keywords
- wobbler
- cylinder block
- type compressor
- disk type
- lug boss
- Prior art date
- Legal status (The legal status 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 status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1063—Actuating-element bearing means or driving-axis bearing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/001—Noise damping
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
A swash plate compressor of the present invention comprises: a housing, a cylinder block which has cylinder bores and is coupled to the housing, pistons which are installed in the respective cylinder bores and able to reciprocate, a drive shaft which is installed to rotate relative to the housing and the cylinder block, and a swash plate which is installed to interlock with the pistons and rotated by the drive shaft. The swash plate compressor also includes a primary support member which is coupled between one side of a swash plate boss and the cylinder block and elastically supports the swash plate, and a secondary support member which is coupled between the other side of the swash plate boss and the cylinder block and rigidly supports the swash plate. Therefore, unstable vibration of the swash plate is effectively restrained by a thrust bearing and a thrust washer and noise is reduced.
Description
Technical field
The present invention relates to a kind of rotating sloping disk type compressor, particularly a kind of unstable vibrational energy of wobbler is effectively controlled to reduce the rotating sloping disk type compressor of noise.
Background technique
Normally, the compartment temperature that the air-conditioning system of vehicle utilizes freezing mixture keeping vehicle is lower than ambient temperature, and it comprises compressor, and condenser and vaporizer are used to form the refrigeration cycle of freezing mixture.
Said compressor compresses with supply with said freezing mixture and power or motoring through motor.
The rotating sloping disk type compressor is a kind of in the reciprocating type compressor; It is arranged so that a dish type wobbler is installed on the live axle; The driving force of motor through said live axle with the corresponding to variable or fixing angle of declination transmission of the rotation of said live axle; And a brake slipper during said wobbler rotation, can make a plurality of piston set in a plurality of casing bore internal linear ground to-and-fro motion that form on the cylinder block along the circumferential arrangement of said wobbler; Suction then, compression and release cooled gas.
Usually, in order to aspirate, to compress and discharging said cooled gas, a valve plate can be installed to allow and to be blocked in the suction between housing and the said cylinder block and to discharge cooled gas.
More particularly, the structure of existing rotating sloping disk type compressor will be made detailed description with reference to Fig. 1 and 2.
As shown in the figure; A kind of existing rotating sloping disk type compressor comprises a pair of cylinder block 10A, 10B; By the live axle 11 of said a pair of cylinder block 10A, 10B supporting; Be installed in the wobbler 12 on the said live axle 11; Around 11 assemblings of said live axle with thrust bearing 13 near said wobbler 12 both sides, the forward and backward housing 14 of the opening end of closed said a pair of cylinder block 10A, 10B and 15 and the through bolt 16 that passes through said a pair of cylinder block 10A, 10B and said forward and backward housing 14,15 that runs through.
Here, through fastening said through bolt 16, the resiliently deformable that is occurred in said live axle 11 axial contour projector on the bearing race of said thrust bearing 13 absorbs, and said bearing race comprises an inner race 13a and an outer race 13b.
In this case; Said inner race 13a is soldered to an annular pressure seat 12a; It is formed in two lug bosses near the said wobbler 12 of external diameter, and said outer race 13b is soldered to annular pressure seat 12a, and it is formed on the support of said cylinder block 10A near internal diameter, 10B.
According to existing rotating sloping disk type compressor; By the rotation of said wobbler 12 causes and compression reaction force through said cooled gas produces thrust load by said thrust bearing 13 supportings; And especially, the both sides of said thrust bearing 13 are had the said annular pressure seat 10a and 12 yielding supports of different-diameter.
That is, the thrust bearing 13 of said existing rotating sloping disk type compressor, as shown in Figure 2, corresponding to the spring S of the both sides that are arranged in said wobbler 12 with the supporting changing load.
Yet when during compression reaction force puts on said wobbler 12 through spring S, producing rotation, said wobbler 12 causes that the frequency component with high speed change that produces during unstable vibration and noise are owing to high speed rotating increases.
In addition, because the complicated structure of said thrust bearing 12, assembling said thrust bearing 13 is difficulties and expensive.
Because the rotation of said wobbler 12, a compressive load is periodically put on the part of said wobbler lug boss.Because existing rotating sloping disk type compressor does not comprise the supplementary equipment of a part of augmenting the lug boss that is applied in compressive load; So the lug boss of wobbler 12 and said cylinder block 10A, 10B will produce local side wear because said compressive load puts on a side of said wobbler 12, to such an extent as between the on-stream period of said compressor, produce noise and vibration.
Therefore, constructed the present invention in view of the above problems, and the unstable vibrational energy that one aspect of the invention provides a kind of wobbler is effectively controlled to reduce the rotating sloping disk type compressor of noise.
Another aspect of the present invention provide one have simple structure the rotating sloping disk type compressor so that reduce production costs.
Another aspect of the present invention provides a kind of rotating sloping disk type compressor, and the part of lug boss that is applied in a wobbler of compressive load during the rotation of wherein said wobbler is augmented lug boss and the concentrated wear of cylinder block by the compressive load generation of a side that puts on said wobbler to prevent said wobbler.
Summary of the invention
According to an aspect of the present invention, above-mentioned and other aspects can be accomplished through a kind of rotating sloping disk type compressor that provides, and the rotating sloping disk type compressor comprises: a housing; Be formed with a plurality of casing bores and be connected to a cylinder block of said housing; Be contained in the said casing bore with corresponding pistons reciprocating group; The live axle that said relatively housing and said cylinder block are rotatably installed; Through rotation of said live axle and the wobbler that links with piston set; Be connected between a side and the said cylinder block of said wobbler flexibly to support first support member of said wobbler; And be connected between another side and the said cylinder block of said wobbler to support second support member of said wobbler rigidly.
In addition, said second support member can stop counterrotating equipment to be connected in the lug boss or the said cylinder block of said wobbler through one.
In addition, the counterrotating equipment of said prevention can comprise: be formed in the joint dimple on any one of lug boss of said second support member and said wobbler; Be formed on another of said second support member and said wobbler lug boss to be contained in the copulational protuberance in the said joint dimple; Be formed in the joint dimple to be in contact with one another on any one of said second support member and said cylinder block; Be formed on another of said second support member and said cylinder block to be contained in the copulational protuberance in the said joint dimple.
In addition, said second support member is a plurality of and is sliding contact.
The second adjacent support member has a guide protrusion and the arc guiding dimple that holds said guide protrusion, and the said second adjacent support member is connected mutually with said guide protrusion through said guiding dimple.
Said second support member comprises the thrust washer of being processed by synthetic resin.
Said second support member comprises the thrust washer that scribbles special teflon (Teflon).
In addition, said first support member is connected in the lug boss or the said cylinder block of said wobbler through stoping counterrotating equipment.
According to another aspect of the present invention, a kind of rotating sloping disk type compressor that provides comprises: a housing; Be formed with a plurality of casing bores and be connected to a cylinder block of said housing; Be contained in the said casing bore with corresponding pistons reciprocating group; The live axle that said relatively housing and said cylinder block are rotatably installed; Through rotation of said live axle and the wobbler that links with piston set; And be connected between a side and the said cylinder block of said wobbler flexibly to support a thrust bearing of said wobbler; The side of wherein said wobbler lug boss and said cylinder block are each other near with mutually supporting and between said lug boss and said cylinder block, scribble special teflon (Teflon) regularly.
In addition, said cylinder block have be formed in above the circumferencial direction to the dimple of said thrust bearing be formed in the dimple of the inside face of said lug boss to said thrust bearing.
According to a further aspect of the invention, a rotating sloping disk type compressor that provides comprises: a housing; Be formed with a plurality of casing bores and be connected to a cylinder block of said housing; Be contained in the said casing bore with corresponding pistons reciprocating group; The live axle that said relatively housing and said cylinder block are rotatably installed; Through rotation of said live axle and the wobbler that links with piston set; Be installed between a side and the said cylinder block of a lug boss of said wobbler to support a thrust bearing of said wobbler; With the rigid support means and the resilient supporting unit of a side that is formed in said wobbler lug boss and another side,, said rigid support means carries out in the zone of a compression stroke and being formed in said piston set.
In addition, when corresponding resilient supporting unit when the running shaft of said live axle is observed around said running shaft symmetry location.
In addition, said resilient supporting unit is to be formed in the concave grooves of said wobbler lug boss so that it contacts with said thrust bearing.
Said resilient supporting unit is formed on the said lug boss and has the angle of circumference in 180 degree to the 315 degree scopes.
In addition, said rigid support means and said resilient supporting unit have support member and are installed on this liner part.
The support member of said rigid support means and said resilient supporting unit comprises the resilient member with different elasticity coefficient.
Said resilient member comprises towards said cylinder block with the crooked leaf spring of the form of a semicircle.
Said rigid support means also comprises the elastic body that is arranged in wherein.
In addition, said liner part has the step of different depth.
According to rotating sloping disk type compressor of the present invention, the vibration of the instability of said wobbler can be controlled through said thrust bearing and said thrust washer effectively, and therefore can also reduce noise.
In addition, simple structure can be kept low production cost.
In addition; When the remaining part except that the part of the lug boss of the wobbler that is applied in compressive load has dimple during wobbler rotation; Perhaps when the lug boss of wobbler has a part that ring liner part and has high-intensity lug boss corresponding to the wobbler that is applied in compressive load and is installed in the spring in the said liner part, can prevent since the compressive load that is applied in towards a side of said wobbler and in the lug boss of wobbler and the concentrated wear of cylinder block generation.
Because the degree of depth of the said liner part that the degree of depth of the said liner part faced of rigid support spring is faced less than the yielding support spring, the lug boss that is applied in the said wobbler of compressive load can be more doughtily by rigid support.
In addition, when an elastomer being installed when overlapping with said rigid support spring, the lug boss of said wobbler can be further by supporting rigidly.
Description of drawings
Description through following examples also combines corresponding accompanying drawing, can understand and be more readily understood the present invention's these and/or other aspect and advantage more, wherein:
Fig. 1 illustrates the side cross-sectional views of a shaft-like rotating sloping disk type compressor;
Fig. 2 illustrates the schematic representation of the load absorption function of a thrust bearing among Fig. 1;
Fig. 3 illustrates the sectional view of embodiment of the present invention first embodiment's a rotating sloping disk type compressor;
Fig. 4 illustrates the perspective view of a cylinder block of embodiment of the present invention first embodiment's said rotating sloping disk type compressor;
Fig. 5 illustrates the sectional view of an example of major component of embodiment of the present invention first embodiment's said rotating sloping disk type compressor;
Fig. 6 illustrates the sectional view of another example of major component of embodiment of the present invention first embodiment's said rotating sloping disk type compressor;
Fig. 7 illustrates the sectional view of another example of major component of embodiment of the present invention first embodiment's said rotating sloping disk type compressor;
Fig. 8 illustrates the sectional view of another example of major component of embodiment of the present invention first embodiment's said rotating sloping disk type compressor;
Fig. 9 illustrates the sectional view of embodiment of the present invention second embodiment's a rotating sloping disk type compressor;
Figure 10 illustrates the sectional view of an example of part A among Fig. 9;
Figure 11 illustrates the sectional view that I-I along the line obtains among Figure 10;
Figure 12 illustrates the sectional view of another example of part A among Fig. 9; With
Figure 13 illustrates the sectional view that II-II along the line obtains among Figure 12.
Embodiment
Hereinafter, embodiment of the present invention embodiment's a rotating sloping disk type compressor will be described in detail with reference to respective drawings.
A rotating sloping disk type compressor 1000 according to the present invention will be applied to the piston compressor of a pair of head, but also can be applied to the single-head piston type compressor.
Embodiment 1
Fig. 3 and 4 shows embodiment of the present invention first embodiment's a rotating sloping disk type compressor 1000.
As shown in the figure; Embodiment of the present invention first embodiment's said rotating sloping disk type compressor 1000 comprises that one has the cylinder block 100 of a plurality of casing bores 110; The casing bore 110 that is contained in said cylinder block 100 is with pistons reciprocating group 200 therein; Be connected to the front and back housing 310,320 of said cylinder block 100 front and back sides, the live axle 400 that said relatively housing 310 and said cylinder block 100 are rotatably installed to seal said front and back sides; Be mounted being connected in the wobbler 500 of said live axle 400 and said piston set 200, and be arranged in said cylinder block 100 and said front and back housing 310, the valve plate between 320 600 accordingly.
As shown in Figure 3, said cylinder block 100 is arranged between said front and back housing 310 and 320, and has a plurality of casing bores 110 so that piston set 200 to-and-fro motion therein.
Said cylinder block 100 has a conjugate foramen 120 and and is installed in the rotary valve R rotating freely in the said conjugate foramen 120.Said rotary valve R is formed on the said live axle 400.
Shown in Fig. 3 and 4; Are the interior all sides that are formed in the said conjugate foramen 120 of the external peripheral surface of facing said rotary valve R to the intercommunicating pore 130 of a plurality of casing bores 110 supply freezing mixtures with it from the freezing mixture suction bole 140 that a wobbler chamber 101 is passed to said housing 310,320.
When said freezing mixture suction bole 140 is arranged between the adjacent casing bore 110, effective coolant.More particularly, said freezing mixture suction bole 140 can be arranged between the said adjacent intercommunicating pore 130 one by one.
Said live axle 400 comprises that one is formed in the freezing mixture bullport 410 that axial freezing mixture release aperture 420 and is connected with said freezing mixture release aperture 420, and it discharges the said freezing mixture that is contained among the coolant reservoir P1 to said rotary valve R via said freezing mixture suction bole 140.
Said freezing mixture bullport 410 possibly be shaped on an axial end or its external peripheral surface of said live axle 400.
Said freezing mixture suction bole 140 interconnects through the said coolant reservoir P1 that is formed on the said front and back housing 310,320 with said freezing mixture bullport 410.
Therefore, the freezing mixture of said suction sequentially passes said wobbler chamber 101, said freezing mixture suction bole 140; Said coolant reservoir P1, said freezing mixture bullport 410, said freezing mixture release aperture 420; Said rotary valve R; Said intercommunicating pore 130 and said casing bore 110 are compressed then.After this, the coolant of said compression is discharged to freezing mixture discharge chamber P2.
Said rotary valve R can an import and an outlet replace, with suction with discharge said freezing mixture.
One first support member is installed between the side and said cylinder block 100 of said wobbler 500, and one second support member is installed between the another side and said cylinder block 100 of said wobbler 500.
First support member possibly be that a thrust bearing 700, the second support members possibly be thrust washers 800.
In more detail, said thrust bearing 700 and said thrust washer 800 are installed in a lug boss 510 of said wobbler 500.
Said thrust bearing 700 comprises an inner race 710, one outer races 720 and is installed in the solid of rotation 730 (ball or a cylindrical body) between said inner race 710 and the said outer race 720.
Said inner race 710 is soldered near the annular pressure seat 501 on the lug boss 510 of the said wobbler 100 of being formed on of external diameter, and said outer race 720 is soldered to the annular pressure seat 102 on the supporting portion that is formed on said cylinder block 100.
In this case; One dimple is formed in the outside of said pressure seat 102 of said cylinder block 100 oppressing the center of said outer race 720, and the excircle end that said pressure seat 501 inner dimples that form that in the said lug boss 510 of said wobbler 500, form are oppressed said inner race 710 is to apply an elastic force when said inner race 710 and 720 bendings of said outer race between said wobbler 500 and said cylinder block 100.
Therefore; 700 supportings of said thrust bearing have the said annular pressure seat 501 and 102 of different-diameter flexibly supporting a side of said wobbler 500, and the another side that said thrust washer 800 supports said wobbler 500 rigidly is with the vibration of controlling said wobbler 500 and prevent noise.
Hereinafter, second support member, promptly said thrust washer 800 will be described with reference to Fig. 5-7.
As shown in the figure, the said thrust washer 800 that adopts among first embodiment comprises that one or at least two thrust washers are to reach sliding contact.
In addition, said thrust washer 800 stops counterrotating equipment to be connected in the lug boss 501 or the said cylinder block 100 of said wobbler 500 through one.
When at least two thrust washers 800 are set; The counterrotating equipment of said prevention can be arranged so that one engages dimple 801 and is formed on any one of lug boss 501 of said thrust washer 800 or said wobbler 500; One copulational protuberance 802 is formed on another so that it is contained in the said joint dimple 801; One engages dimple 801 is formed on arbitrary thrust washer 800 it is contacted with each other, and the copulational protuberance 802 that is contained in the said joint dimple 801 is formed on another.
Therefore, of at least two thrust washers 800 is fixed on the said cylinder block 100 and another is fixed in said wobbler 500 and rotates thereupon, so that only said thrust washer 800 is relative to each other so that slide over each other contact.
Usually, said thrust washer 800 is formed from steel, and said cylinder block 100 and said wobbler 500 processed by aluminum alloy, and does not directly contact with said aluminum alloy for the steel that prevents to wear and tear.
In addition; Said joint dimple 801 possibly be formed on the side and another side of said thrust washer 800 with said copulational protuberance 802 respectively, and perhaps said joint dimple 801 maybe be all shapeless on the side of said thrust washer 800 with said copulational protuberance 802.
Shown in Fig. 6 and 7, when at least two thrust washers 800 were set, any one of adjacent two thrust washers 800 can have a guiding dimple 803, and another does not have said guiding dimple 803 but has the guide protrusion 804 towards said guiding dimple 803.That is, said guiding dimple 803 combines said guide protrusion 804 to be separated from each other to prevent said at least two thrust washers 800.
As shown in the figure, said guiding dimple 803 is circular with said guide protrusion 804.
It is as shown in Figure 7 when three thrust washers 800 are set; Be arranged on the said thrust washer 800 of both sides because the joint between said joint dimple 801 and said copulational protuberance 802 will be by said cylinder block 100 and said wobbler 500 supportings; And when said rounded leading dimple 803 and said rounded leading projection 804 engage one another when preventing to separate, the thrust washer 800 of said centre is by said two thrust washers, 800 supportings.
Said thrust washer 800 is processed such as polyether-ether-ketone (PEEK) by the synthetic resin with excellent heat resistance and fatigue resistance, and can make the wearing and tearing of the said wobbler 500 that is caused by high speed rotating reduce to minimum.
In addition, said thrust washer 800 has applied special teflon teflon (Teflon PTEE) with low frictional factor so that the kinetic equation loss that is caused by friction reduces to minimum.
In addition, first support member can be that thrust washer 800 and its explanation will be omitted.
As shown in Figure 8, the surperficial coated special teflon of the surface of opposed facing said cylinder block 100 and said wobbler 500 with each other near with each other rigidly the supporting.
Embodiment 2
Embodiment of the present invention second embodiment's a rotating sloping disk type compressor is shown in Fig. 9-13.
As shown in Figure 9; Embodiment of the present invention second embodiment's a rotating sloping disk type compressor comprises that one has the cylinder block 110 of a plurality of casing bores 100; Be contained in the casing bore 100 of said cylinder block 110 with reciprocating piston set 120; The front and back sides that connects said cylinder block 110 is with the front and back housing 130,140 of the front and back sides that seals said cylinder block 110; The live axle 150 that said relatively front case 130 and said cylinder block 110 are rotatably installed, the wobbler 160 that installation makes itself and said live axle 150 be connected with piston set 120, and be arranged in said cylinder block 110 and said front and back housing 130, the valve plate between 140 170.
Said cylinder block 110 is arranged in said front and back housing 130, between 140, and comprise a front end cylinder block 111 and a rear end cylinder block 112 that is arranged on a side of said rear case 140 of a side that is arranged on said front case 130.One wobbler chamber is formed between said front end cylinder block 111 and the said rear end cylinder block 112, and each of cylinder block 111 and 112 all has a plurality of casing bores 100 so that piston set 120 to-and-fro motion.
Simultaneously, said cylinder block 110 has a conjugate foramen 113, and said live axle 150 is through wherein.One rotary valve R is mounted to be free to slide or to be formed on the part of said live axle 150 on the said live axle 150.
In addition, be formed in interior all sides of the said conjugate foramen 113 of the external peripheral surface of facing said rotary valve R to corresponding casing bore 100 intercommunicating pore 114 of supplying with freezing mixtures and the freezing mixture suction bole (not shown) that is connected wobbler chamber and said housing.
When said freezing mixture suction bole is arranged between the adjacent casing bore, effective coolant.
Said live axle 150 has one and is formed in the freezing mixture bullport 152 that said live axle 150 axial freezing mixture release aperture 151 and are connected with said freezing mixture release aperture 151, and said freezing mixture bullport 152 discharges and passes said freezing mixture suction bole and be stored in freezing mixture among the said coolant reservoir P1 to said rotary valve R.
Said freezing mixture bullport 152 possibly be shaped on the external peripheral surface of an axial end of said live axle 150 or said live axle 150.
Said freezing mixture suction bole and said freezing mixture bullport 152 interconnect through the said coolant reservoir P1 that is formed on the said front and back housing 130,140.
Therefore, the said freezing mixture from said freezing mixture suction ports suction sequentially passes said wobbler chamber, said freezing mixture suction bole; Said coolant reservoir P1, said freezing mixture bullport 152, said freezing mixture release aperture 151; Said rotary valve R, said intercommunicating pore 114 and said casing bore 100; And in said casing bore 100, be compressed, said then compressed freezing mixture is discharged to said freezing mixture discharge chamber P2.
Simultaneously, replace said rotary valve R, can on a valve plate, form an import and an outlet in order to suction with discharge said freezing mixture.
Between said wobbler 160; Promptly; Between the lug boss 161 and said cylinder block 110 of said wobbler 160, a thrust bearing 180 is mounted with the said wobbler 160 of supporting during the suction of the piston set 120 that causes in the rotation by said wobbler 160 and the compression stroke.
Shown in figure 10, said thrust bearing 180 comprises an inner race 181, one outer races 182 and is installed in the solid of rotation 183 (ball or a cylindrical body) between said inner race 181 and the said outer race 182.
One dimple is formed in the outside of said cylinder block 110 in the face of said outer race 182, and annular first pressure seat 116 be formed in said cylinder block 110 the inboard so that the inboard of said cylinder block 110 can contact flexibly to support said wobbler 160 with said outer race 182 parts through dimple.
First example according to a second embodiment of the present invention, shown in figure 10, a rigid support and a yielding support are formed on the side and another side of lug boss 161 of said wobbler 160.
Said rigid support is formed in the part that piston set is carried out compression stroke.
Said yielding support can be to be formed in a arcuate furrow 210 on the lug boss 161 of said wobbler 160 so that contact with said thrust bearing 180.
That is, during the to-and-fro motion that is rotated in piston set 120 through said live axle 150, said compressive load is not the whole both sides that periodically are applied to said lug boss 161, but is applied to a presumptive area of said lug boss 161 both sides.In this case, said groove 210 is formed in the remaining part except that the said presumptive area that is applied in compressive load.
Corresponding yielding support; Promptly; When the running shaft of said live axle 150 is observed, partially-formed said groove 210 in said lug boss 161 1 sides and the running shaft symmetry location of partially-formed said groove 210 in said lug boss 161 another sides around said live axle 150.
This is why said compressive load is by periodic or put on the presumptive area of the corresponding symmetry in said lug boss 161 both sides simultaneously, and a be not shaped side and the said inner race of said lug boss 161 above that of said groove 210 contacts the part of both sides of the lug boss 161 of the said wobbler 160 that is applied simultaneously with the rigid support compressive load fully.
In addition, the said lug boss 161 that is adjacent to said groove 210 provides one than the said groove 210 outstanding second higher pressure seats 162.
Three countercylinder holes 100 are faced with piston set 120 each other in an example; Shown in figure 11; One yielding support, promptly said groove 210, circumferential lengths D1 within 1/2 to 7/8 scope of the circumferential lengths of a imaginary circle with radius of curvature identical with groove 210.Especially, said groove 210 has the angle of circumference in 180 degree to the 315 degree scopes.
In addition, said scope can the circumferential lengths of said imaginary circle 3/4 to 5/6 within.
If the circumferential lengths D1 of said groove 210 exceeds said scope, a zone of the lateral parts of the said lug boss 161 that can not be shaped at said groove 210 can excessively dwindle or increase so that the part of the lug boss 161 of said wobbler 160 can not be by a wide part of rigid support or said lug boss 161 completely by supporting rigidly during the compression stroke of piston set 120.
Yet the present invention is not limited thereto and the above-mentioned scope of mentioning can change according to the quantity of said casing bore 100 and piston set 120.
In first example of second embodiment of the invention, the part of the lug boss 161 of the said wobbler 160 that can not be shaped at said groove 210 makes and during the compression stroke of said piston set 120, contacts fully so that said wobbler 160 can be by supporting rigidly with said inner race 181.
On the other hand; When second pressure seat 162 is formed in the 161 last times of said lug boss in abutting connection with said groove 210; It makes and contacts to oppress the outside of said outer race 182 with said inner race 181; And be formed in 110 last times of said cylinder block when first pressure seat 116 simultaneously; It oppresses the inboard of said inner race 181 because said elastic force is applied between said wobbler 160 and the said cylinder block 110, from the said thrust bearing 189 in the face of the part of the said lug boss 161 that do not apply compressive load produce flexural stresses in case said wobbler 160 by flexible supporting.
Therefore; A part that during said wobbler 160 rotations, applies the said wobbler 160 of compressive load is supported the concentrated wear that produces from the lug boss 161 of said live axle 150 and said wobbler 160 to prevent more reliably, and the noise and the vibration of generation during the control rotation when said concentrated wear has produced.
Second example according to second embodiment of the invention; Shown in Figure 12 to 13; Said rigid support and said yielding support are formed separately on a side and another side of the lug boss 161 of said wobbler 160; So that loop concave liner part 220 is formed on said rigid support and the said yielding support with towards said thrust bearing 180, and support member is installed in said liner part to support said wobbler 160.
Said support member can be the resilient member with a predetermined elasticity, and particularly spring 300.
Said resilient member; Promptly; Said spring 300; As first example of second embodiment, comprise the arc rigid support spring 310 of a part of the lug boss 161 of the said wobbler 160 of rigid support, the above-mentioned part of said lug boss 161 for during the compression stroke of said piston set 120 because the rotation of said wobbler 160 is applied in the part of compressive load; With an arc yielding support spring 320 of the remaining part of the said lug boss of yielding support, the remaining part of said lug boss is the part except that the lug boss 161 of the said wobbler 160 that is applied in compressive load.
When observing from the longitudinal section of said live axle 150, said spring 300 can be with the crooked guiding spring of the form of semicircle, so that said spring 300 enough supports said wobbler 160 during said wobbler 160 rotations towards said cylinder block.
Said rigid support spring 310; As first embodiment; Can have the spring rate bigger, so that rigid support is applied in a part and the remaining part of the said lug boss 161 of yielding support of the said lug boss 161 of compressive load than said yielding support spring 320.
In this case; Another elastic devices (not shown) can be set to overlap with the position of said rigid support spring 310 at a rigid support; Promptly; Said rigid support spring 310 is disposed in the said liner part 220, and for example rigid support is applied in the part of lug boss 161 of the said wobbler 160 of compressive load.
Therefore, but the said elastic devices (not shown) of additional configuration so that the spring rate of said rigid support spring 310 can increase.
In another example, said liner part 220 can have the step of different depth.
That is, the degree of depth of said liner part 220 can be inequality, and in other words, the depth d 1 of the said liner part 220 that contacts with said rigid support spring 310 maybe be less than the depth d 2 of the said liner part 220 that contacts with said yielding support spring 320.
Therefore; When the identical compressive load of supposition during 160 rotations of said wobbler was periodically put on said lug boss 161, the initial pressure of said rigid support spring 310 was that the spring rate of huge and said rigid support spring 310 can increase relatively.
In second example of second embodiment; As second example of second embodiment; When three countercylinder holes 100 and piston set 120 each other in the face of the time, the circumferential lengths of said rigid support spring 310 is within 1/8 to 1/2 scope of the whole circumferential lengths of said liner part 220.
Especially, the angle of circumference of said rigid support spring 310 is within 45 degree to the scope of 180 degree.
In addition, said scope can be within 1/6 to 1/4 scope of the whole circumferential lengths of said liner part 220.
If the circumferential lengths of said rigid support spring 310 exceeds said scope, the part of the lug boss 161 of said wobbler 160 can perhaps be had other part of rigid support to be supported consequently owing to concentrated wear produces noise and vibration rigidly by rigid support exactly during the compression stroke of piston set 120.
The present invention has showed and has described the content relevant with exemplary embodiments that the improvement of its generation and variation will become apparent to those skilled in the art that and do not break away from thought of the present invention and the scope that limits like accessory claim.
Claims (19)
1. rotating sloping disk type compressor comprises:
One housing;
Be formed with a plurality of casing bores and be connected to a cylinder block of said housing;
Be contained in the said casing bore with corresponding pistons reciprocating group;
The live axle that said relatively housing and said cylinder block are rotatably installed;
Through rotation of said live axle and the wobbler that links with piston set;
Be connected between a side and the said cylinder block of said wobbler flexibly to support one first support member of said wobbler; With
Be connected between another side and the said cylinder block of said wobbler to support one second support member of said wobbler rigidly.
2. rotating sloping disk type compressor as claimed in claim 1, wherein second support member stops counterrotating equipment to be connected in the lug boss or the said cylinder block of said wobbler through one.
3. rotating sloping disk type compressor as claimed in claim 2, the counterrotating equipment of wherein said prevention comprises:
Be formed in one on any one of lug boss of said second support member and said wobbler and engage dimple;
Be formed on another of lug boss of said second support member and said wobbler to be contained in the copulational protuberance in the said joint dimple;
Be formed on any one of said second support member and said cylinder block so that both be in contact with one another one engage dimple; With
Be formed on another of said second support member and said cylinder block to be contained in the copulational protuberance in the said joint dimple.
4. according to claim 1 or claim 2 rotating sloping disk type compressor, wherein said second support member is a plurality of and is sliding contact.
5. rotating sloping disk type compressor as claimed in claim 4; The second wherein adjacent support member has a guide protrusion and the arc guiding dimple that holds said guide protrusion, and the said second adjacent support member is connected mutually with said guide protrusion through said guiding dimple.
6. rotating sloping disk type compressor as claimed in claim 4, wherein said second support member comprise the thrust washer processed by synthetic resin.
7. rotating sloping disk type compressor as claimed in claim 4, wherein said second support member comprise that one scribbles the thrust washer of special teflon (Teflon).
8. rotating sloping disk type compressor as claimed in claim 4, wherein said first support member stops counterrotating equipment to be connected in the lug boss or the said cylinder block of said wobbler through one.
9. rotating sloping disk type compressor comprises:
One housing;
Be formed with a plurality of casing bores and be connected to a cylinder block of said housing;
Be contained in the said casing bore with corresponding pistons reciprocating group;
The live axle that said relatively housing and said cylinder block are rotatably installed;
Through rotation of said live axle and the wobbler that links with piston set; With
Be connected between a side and the said cylinder block of said wobbler flexibly to support a thrust bearing of said wobbler;
The side of the lug boss of wherein said wobbler and said cylinder block are each other near with mutually supporting and between said lug boss and said cylinder block, scribble special teflon regularly.
10. rotating sloping disk type compressor as claimed in claim 9, wherein said cylinder block have be formed in above the circumferencial direction to a dimple of said thrust bearing be formed in the dimple of the inside face of said lug boss to said thrust bearing.
11. a rotating sloping disk type compressor comprises:
One housing;
Be formed with a plurality of casing bores and be connected to a cylinder block of said housing;
Be contained in the said casing bore with corresponding pistons reciprocating group;
The live axle that said relatively housing and said cylinder block are rotatably installed;
Through rotation of said live axle and the wobbler that links with piston set;
Be installed between a side and the said cylinder block of a lug boss of said wobbler to support a thrust bearing of said wobbler; With
Rigid support means and resilient supporting unit are formed in a side and the another side of the lug boss of said wobbler, and said rigid support means is formed in said piston set and carries out in the zone of a compression stroke.
12. rotating sloping disk type compressor as claimed in claim 11, wherein when corresponding resilient supporting unit when the running shaft of said live axle is observed around said running shaft symmetry location.
13. rotating sloping disk type compressor as claimed in claim 11, wherein said resilient supporting unit are to be formed in concave grooves on the lug boss of said wobbler so that it contacts with said thrust bearing.
14. rotating sloping disk type compressor as claimed in claim 11, wherein said resilient supporting unit are formed on the said lug boss and have the angle of circumference in one 180 degree to the 315 degree scopes.
15. rotating sloping disk type compressor as claimed in claim 11, wherein said rigid support means and said resilient supporting unit have support member and are installed on this liner part.
16. rotating sloping disk type compressor as claimed in claim 15, the support member of wherein said rigid support means and said resilient supporting unit comprises the resilient member with different elasticity coefficient.
17. rotating sloping disk type compressor as claimed in claim 15, wherein said resilient member comprise towards said cylinder block with the crooked leaf spring of the form of a semicircle.
18. rotating sloping disk type compressor as claimed in claim 16, wherein said rigid support means also comprises the elastic body that is arranged in wherein.
19. rotating sloping disk type compressor as claimed in claim 15, wherein said liner part has the step of different depth.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2009-0000664 | 2009-01-06 | ||
| KR1020090000664A KR100964532B1 (en) | 2009-01-06 | 2009-01-06 | Swash pate type compressor |
| KR10-2009-0003022 | 2009-01-14 | ||
| KR1020090003022A KR101030213B1 (en) | 2009-01-14 | 2009-01-14 | Swash plate type compressor |
| PCT/KR2010/000048 WO2010079939A1 (en) | 2009-01-06 | 2010-01-06 | Swash plate compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102341599A true CN102341599A (en) | 2012-02-01 |
Family
ID=42316637
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010800104509A Pending CN102341599A (en) | 2009-01-06 | 2010-01-06 | Swash plate compressor |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN102341599A (en) |
| WO (1) | WO2010079939A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105804965A (en) * | 2015-01-21 | 2016-07-27 | 株式会社丰田自动织机 | Double-headed piston type swash plate compressor |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1131730A (en) * | 1994-11-22 | 1996-09-25 | 株式会社丰田自动织机制作所 | Bearing arrangement in swash plate type compressor with double headed pistons |
| CN1132314A (en) * | 1994-11-18 | 1996-10-02 | 株式会社丰田自动织机制作所 | Double-headed swash-plate operated reciprocating piston type compressor with improved thrust bearing assemblies for swash plate |
| JPH08261148A (en) * | 1995-03-22 | 1996-10-08 | Toyota Autom Loom Works Ltd | Double head swash plate type compressor |
| JPH0960586A (en) * | 1995-08-21 | 1997-03-04 | Toyota Autom Loom Works Ltd | Cam plate-type double ended compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5392710U (en) * | 1976-12-28 | 1978-07-28 | ||
| KR20060032487A (en) * | 2004-10-12 | 2006-04-17 | 엘지전자 주식회사 | Rotation prevention device of scroll compress |
-
2010
- 2010-01-06 CN CN2010800104509A patent/CN102341599A/en active Pending
- 2010-01-06 WO PCT/KR2010/000048 patent/WO2010079939A1/en active Application Filing
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1132314A (en) * | 1994-11-18 | 1996-10-02 | 株式会社丰田自动织机制作所 | Double-headed swash-plate operated reciprocating piston type compressor with improved thrust bearing assemblies for swash plate |
| CN1131730A (en) * | 1994-11-22 | 1996-09-25 | 株式会社丰田自动织机制作所 | Bearing arrangement in swash plate type compressor with double headed pistons |
| JPH08261148A (en) * | 1995-03-22 | 1996-10-08 | Toyota Autom Loom Works Ltd | Double head swash plate type compressor |
| JPH0960586A (en) * | 1995-08-21 | 1997-03-04 | Toyota Autom Loom Works Ltd | Cam plate-type double ended compressor |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105804965A (en) * | 2015-01-21 | 2016-07-27 | 株式会社丰田自动织机 | Double-headed piston type swash plate compressor |
| CN105804965B (en) * | 2015-01-21 | 2017-12-22 | 株式会社丰田自动织机 | Double-headed piston type swash plate compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2010079939A1 (en) | 2010-07-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA2174403C (en) | Refrigerant compressor having improved drive power transmission unit | |
| US7416343B2 (en) | Pulley support double row ball bearing | |
| US5768974A (en) | Swash plate type compressor | |
| US20050156386A1 (en) | Sealing device and compressor | |
| US6612813B2 (en) | Power transmission mechanism | |
| JP2005264943A (en) | Swash plate type compressor with swash plate tilted at given angle | |
| US20090220355A1 (en) | Swash plate compressor | |
| CN102341599A (en) | Swash plate compressor | |
| US8137078B2 (en) | Axial piston machine | |
| EP3147502B1 (en) | Bidirectional wobble plate compressor | |
| US6393964B1 (en) | Compressor having piston rotation restricting structure with lubricating inclined guide surface | |
| US6276905B1 (en) | Piston-shoe arrangement for a swash plate compressor | |
| US5737997A (en) | Cam plate supporting structure in a cam plate type compressor | |
| US8303263B2 (en) | Swash plate type compressor | |
| KR20170037219A (en) | Swash plate type compressor for vehicle | |
| JPH10213062A (en) | Variable displacement swash plate compressor | |
| KR100964532B1 (en) | Swash pate type compressor | |
| KR20130074388A (en) | Compressor | |
| US20140241925A1 (en) | Swash plate compressor | |
| KR100274970B1 (en) | Variable displacement swash plate compressor | |
| KR20170035083A (en) | Swash plate compressor | |
| JP2007218162A (en) | Reciprocating type fluid machine | |
| JP2007009886A (en) | Compressor | |
| KR20100031409A (en) | Swash-plate type compressor | |
| JPH10205437A (en) | Swash plate for swash plate type compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20120201 |