CN101886623A - Fixed displacement piston type compressor - Google Patents
Fixed displacement piston type compressor Download PDFInfo
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- CN101886623A CN101886623A CN2010101739046A CN201010173904A CN101886623A CN 101886623 A CN101886623 A CN 101886623A CN 2010101739046 A CN2010101739046 A CN 2010101739046A CN 201010173904 A CN201010173904 A CN 201010173904A CN 101886623 A CN101886623 A CN 101886623A
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- cylinder body
- crank chamber
- ring
- swash plate
- passage
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- 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
Abstract
The present invention relates to a kind of compressor, comprise running shaft, swash plate, cylinder body, a plurality of piston, crank chamber, housing, a plurality of passage, thrust bearing and anti-rotation mechanism.Crank chamber is held swash plate therein, and the refrigeration agent with suction pressure is introduced in the crank chamber.Housing is connected to cylinder body and forms suction chamber and discharge the chamber in housing.Provide a plurality of passages to be communicated with between crank chamber and the suction chamber.Thrust bearing is arranged between swash plate and the cylinder body with the thrust load of carrying from swash plate.Thrust bearing has the back-up ring with the adjacent setting of cylinder body.Provide anti-rotation mechanism in case Sealing shield ring rotates with respect to cylinder body.Anti-rotation mechanism limits the fluid stream that flows through in the special modality in a plurality of passages.
Description
Technical field
The present invention relates to a kind of fixed displacement piston type compressor, have swash plate in the crank chamber of this fixed displacement piston type compressor, treat that compressed refrigeration agent is passed to suction chamber from crank chamber by a plurality of passages.
Background technique
Known a kind of fixed displacement piston type compressor, this fixed displacement piston type compressor have be used for a plurality of passages and the thrust bearing that are communicated with between crank chamber and suction chambers.Thrust bearing is arranged between swash plate and the cylinder body and in a side adjacent with cylinder body has back-up ring.In this compressor,, so need prevent of this rotation of the back-up ring of thrust bearing with respect to cylinder body because back-up ring causes the cylinder body wearing and tearing with respect to the rotation of cylinder body because of between the two sliding contact.In addition, for example as required the function of some special modalities in a plurality of passages is limited, wait to be stored in the amount of the lubricant oil in the crank chamber and the compression in each pressing chamber is equated with increase.
Examining the Japanese Utility Model spy drives among the No.7-10474 disclosed compressor and has and be used to prevent the mechanism of the back-up ring of thrust bearing with respect to this rotation of cylinder body.Compressor comprises: swash plate, and it is with respect to the axis tilt of the running shaft of compressor and can be around the axis rotation of the running shaft of compressor; Piston, it is arranged on from the axis of running shaft spaced positions and can be with the rotation of swash plate along described axis to-and-fro motion radially; And cylinder body, hold piston in the described cylinder body.Between cylinder body and swash plate, be provided with thrust bearing.The back-up ring adjacent with cylinder body of thrust bearing has recess, and cylinder body has the projection that can engage with described recess.Recess prevents the rotation of thrust bearing with respect to cylinder body with engaging of projection, thus the wearing and tearing between anti-Sealing shield ring and the cylinder body.
Careful Japan Patent spy opens No.2000-297745 and discloses another kind of compressor, and in this compressor, being used in a plurality of passages limited refrigeration agent from the function that crank chamber is delivered to some special modalities of suction chamber.In this compressor, suction chamber is connected to inlet by crank chamber, refrigeration agent is transported to a plurality of pressing chambers from described suction chamber, inlet is connected to the vaporizer in the external refrigeration loop of compressor again, and in this compressor, refrigeration agent is transported to the suction chamber by crank chamber from inlet.Be used for that refrigeration agent is delivered to a plurality of passages of suction chamber from crank chamber, the passage that crank chamber is led in the position above running shaft has flow resistance, and this flow resistance is led to the flow resistance of the passage of crank chamber less than the position below running shaft.In this case, the amount that flows to the refrigeration agent in the suction chamber by upper channel has prevented like this that greater than the amount that flows to the refrigeration agent in the suction chamber by lower passage a large amount of liquid refrigerants from flowing in the suction chamber.
But, open among the No.7-10474 in the disclosed compressor examining the Japanese Utility Model spy, only provide in the back-up ring that lays respectively at thrust bearing and cylinder body in recess and projection in case Sealing shield ring with respect to the rotation of cylinder body.On the other hand, open among the No.2000-297745 in the disclosed compressor examining the Japan Patent spy, only provide compressor as the part of the throttle valve that limits channel function to provide and to reduce the channel diameter identical functions.
The present invention aims to provide a kind of fixed displacement piston type compressor, and this fixed displacement piston type compressor prevents that the back-up ring of thrust bearing from rotating with respect to cylinder body, also limits the function of special modality.
Summary of the invention
According to an aspect of the present invention, fixed displacement piston type compressor comprises running shaft, swash plate, cylinder body, a plurality of piston, crank chamber, housing, a plurality of passage, thrust bearing and anti-rotation mechanism.Swash plate is fixed to running shaft.Cylinder body supporting rotating shaft and have a plurality of cylinders hole around running shaft location.A plurality of pistons are contained in the corresponding cylinder hole.Piston is attached to running shaft by swash plate.Crank chamber is held swash plate therein, and the refrigeration agent with suction pressure is introduced in the crank chamber.Housing is connected to cylinder body and forms suction chamber and discharge the chamber in housing.Provide a plurality of passages to be communicated with between crank chamber and the suction chamber.Thrust bearing is arranged between swash plate and the cylinder body with the thrust load of carrying from swash plate.Thrust bearing has the back-up ring with the adjacent setting of cylinder body.Provide anti-rotation mechanism in case Sealing shield ring rotates with respect to cylinder body.Anti-rotation mechanism limits the fluid stream that flows through in the special modality in a plurality of passages.
Carry out in conjunction with the drawings and principle of the present invention is carried out the following description of exemplary description, other aspects and advantages of the present invention will be apparent.
Description of drawings
Fig. 1 is the longitudinal sectional view of the fixed displacement piston type compressor of first embodiment of the invention;
Fig. 2 A is the cross-sectional view along the line IIA-IIA of Fig. 1, wherein shows the back-up ring of thrust bearing of the compressor of Fig. 1;
Fig. 2 B and Fig. 2 category-A seemingly, but wherein show the cross section of the compressor that back-up ring is removed;
Fig. 3 A is the cross-sectional view that the line IIIA-IIIA along Fig. 1 obtains, and wherein shows the back-up ring of another thrust bearing of the compressor of Fig. 1;
Fig. 3 B and Fig. 3 category-A seemingly, but wherein show the cross section of the compressor that back-up ring is removed;
Fig. 4 A is the partial sectional view of fixed displacement piston type compressor second embodiment of the invention; And
Fig. 4 B is the front elevation from the back-up ring of the thrust bearing of the compressor of Fig. 4 A of the swash plate observation of Fig. 4 A.
Embodiment
Fig. 1 shows the fixed displacement piston type compressor of first embodiment of the invention.It should be noted that front side and rear side that the left-hand side observed among Fig. 1 and right-hand side are compressor respectively, and the upside of observing among Fig. 1 and downside are upside and the downside of compressor when installation in position respectively.
Compressor has a pair of cylinder body 11 and 12 that is connected to front case 13 and rear case 16 respectively.Front case 13 and rear case 16 are fastened to cylinder body 11 and 12 by using a plurality of bolts 19 (only illustrating among Fig. 1), and each in a plurality of bolts 19 has the threaded end 19A of external belt.Each bolt 19 inserts and passes bolt hole 13A, 11A and the 12A that is formed at respectively in front case 13, the cylinder body 11 and 12, thereby screwed end 19A is threaded onto among the tapped hole 16A that is formed in the rear case 16.
Between the end face 11B of the annular base 36A of swash plate 36 and cylinder body 11, be provided with thrust bearing 46, between the end face 12B of the base portion 36A of swash plate 36 and cylinder body 12, be provided with thrust bearing 47.
Thrust bearing 11 is formed with inlet 38, and crank chamber 37 is communicated with external refrigerant loop (not shown) by this inlet 38.Cylinder body 11 is formed with a plurality of passages 39 (referring to Fig. 2 A and Fig. 2 B) that run through wherein, a plurality of passages 39 are connected to crank chamber 37 suction chamber 15 of front case 13, similarly, cylinder body 12 is formed with a plurality of passages 49 (referring to Fig. 3 A and Fig. 3 B) that run through wherein, and a plurality of passages 49 are connected to crank chamber 37 suction chamber 18 of rear case 16.
With reference to Fig. 2 A, 2B, 3A and 3B, cylinder body 11 is formed with a plurality of cylinders hole 40 of arranging around running shaft 32, and similarly, cylinder body 12 is formed with a plurality of cylinders hole 50 of arranging around running shaft 32.Match to hold double-head piston 44 in the two in the cylinder hole 50 relative with it, each cylinder hole 40.The front end of double-head piston 44 limits pressing chamber 41 in cylinder hole 40, the rear end of double-head piston 44 limits pressing chamber 51 in cylinder hole 50.Swash plate 36 has a pair of boots 45 for each piston 44, and paired boots 45 are used for rotatablely moving of swash plate 36 is passed to piston 44.
The part that contacts with running shaft 32 of the interior perimeter surface of axis hole 34 is as sealing surfaces 42, and the part that contacts with running shaft 32 of the interior perimeter surface of axis hole 35 is also as sealing surfaces 52.By the sealing surfaces 42 of axis hole 34 and 35 and 52 diameter of a circles that limited diameter less than the other parts of axis hole 34 and 35.Therefore, running shaft 32 directly is bearing on the sealing surfaces 42 and 52 of cylinder body 11 and 12.
The part that is centered on by sealing surfaces 42 and 52 of running shaft 32 is used as rotary valve.Running shaft 32 has aperture 57 and 58 in its periphery.Aperture 57 and 58 is radially aimed at passage 60 and 61 respectively, and this passage 60 and 61 is formed to run through the base portion 36A of swash plate 36.The service duct 54 of running shaft 32 by aperture 57 and 58 and passage 60 and 61 be communicated with crank chamber 37.Running shaft 32 is formed with passage 59, and passage 59 is connected to space 48 with service duct 54.
Thrust bearing 46 comprises: annular retaining ring 62, and the base portion 36A of itself and swash plate 36 is adjacent; Annular retaining ring 63, the end face 11B of itself and cylinder body 11 is adjacent; And a plurality of cylindrical roller 64, it is arranged between back-up ring 62 and 63.Thrust bearing 47 comprises: annular retaining ring 65, and the base portion 36A of itself and swash plate 36 is adjacent; Annular retaining ring 66, the end face 12B of itself and cylinder body 12 is adjacent; And a plurality of cylindrical roller 67, it is arranged between back-up ring 65 and 66.
In the present embodiment, shown in Fig. 2 A and 3A, compressor has anti-rotation mechanism 70 and 71 and anti-rotation mechanism 80 and 81, the back-up ring 63 that anti-rotation mechanism 70 and 71 is used to prevent thrust bearing 46 is with respect to cylinder body 11 rotations, and anti-rotation mechanism 80 and 81 is used to prevent that the back-up ring 66 of thrust bearing 47 is with respect to cylinder body 12 rotations.
The back-up ring 63 adjacent that Fig. 2 A shows thrust bearing 46, Fig. 2 B and Fig. 2 category-A with cylinder body 11 seemingly, its guide ring 63 is removed from cylinder body 11.In the drawings, for simplicity, and not shown double-head piston 44.As shown in the figure, the opening that leads to crank chamber 37 of each passage 39 is around back-up ring 63 location, and back-up ring 63 has two projections 72 and 73, two projections 72 and 73 and extends radially outwardly above being formed at the opening of periphery with the special modality 39 in a plurality of passages 39 of back-up ring.72 pairs of projections in a plurality of passages 39 with inlet 38 immediate passages 39 in the fluid stream that flows through limit.73 pairs of projections limit when the fluid stream that compressor flows through in minimum that passage 39 (the minimum passage 39 in position in Fig. 2) in position in a plurality of passages 39 during installation in position in vehicle.Particularly, the special modality 39 that is associated with projection 73 is that its opening that leads to crank chamber 37 is positioned when compressor that passage of viewed extreme lower position vertically during installation in position in vehicle, and the special modality 39 that is associated with projection 72 is its opening that leads to crank chamber 37 38 immediate those passages that are positioned to and enter the mouth.Be provided with gap (referring to Fig. 1) between the projection 72 (73) of the back-up ring 63 of the opening of special modality 39 and thrust bearing 46.
The back-up ring 66 adjacent that Fig. 3 A shows thrust bearing 47, Fig. 3 B and Fig. 3 category-A with cylinder body 12 seemingly, its guide ring 66 is removed from cylinder body 12.In the drawings, for simplicity, and not shown double-head piston 44.As shown in the figure, the opening that each passage 49 leads to crank chamber 37 is around back-up ring 66 location, and back-up ring 66 has two projections 82 and 83, two projections 82 and 83 and extends radially outwardly above being formed at the opening of periphery with the special modality 49 in a plurality of passages 49 of back-up ring.82 pairs of projections in a plurality of passages 49 with inlet 48 immediate passages 49 in the fluid stream that flows through limit.83 pairs of projections limit when the compressor fluid stream that minimum that passage 49 (the minimum passage 49 in position in Fig. 3) flows through in the position of a plurality of passages 49 during installation in position in vehicle.Particularly, the special modality 49 that is associated with projection 83 is vertically to observe that passage that its opening that leads to crank chamber 37 is positioned extreme lower position during installation in position when compressor in vehicle, and the special modality 49 that is associated with projection 82 is its opening that leads to crank chamber 37 38 immediate those passages that are positioned to and enter the mouth.Be provided with gap (referring to Fig. 1) between the projection 82 (83) of the back-up ring 66 of the opening of special modality 49 and thrust bearing 47.
In above-mentioned compressor, when running shaft 32 being rotated with swash plate 36 from unshowned drive source drives power, rotatablely moving of swash plate 36 is passed to double-head piston 44 by boots 45, makes the to-and-fro motion in the cylinder hole 40 and 50 that it is associated of each double-head piston 44.Refrigeration agent with suction pressure (suction pressure) 38 is introduced into the crank chamber 37 from the external refrigeration loop by entering the mouth, and then by passage 60 and 61 and aperture 57 and 58 flow in the service duct 54.The part of refrigerant that is introduced in the crank chamber 37 is transported in suction chamber 15 and 18 by passage 39 and 49.Refrigeration agent in the suction chamber 15 is introduced in the service duct 54 by passage 13B, space 48 and passage 59.Refrigeration agent in the suction chamber 18 is introduced directly in the service duct 54.
When double-head piston 44 is in induction stroke for cylinder hole 40, that is, when double-head piston in Fig. 1 44 moved right, the outlet 55A of passage 55 was connected to the inlet 43A of passage 43.Refrigeration agent in the passage 54 of running shaft 32 is introduced in the pressing chamber 41 that is in the cylinder hole 40 by passage 55 and 43.
When double-head piston 44 is in discharge stroke for the first cylinder hole 40, that is, when double-head piston in Fig. 1 44 was moved to the left, the outlet 55A of passage 55 disconnected with the inlet 43A of passage 43 and being connected.Refrigeration agent in the pressing chamber 41 is discharged in the discharge chamber 14 by exhaust port 21 when pushing expulsion valve 23 open.Being discharged to the refrigeration agent of discharging in the chamber 14 flows in the external refrigerant loop then.The refrigeration agent that flows through the external refrigerant loop 38 is back to crank chamber 37 by entering the mouth then.
When double-head piston 44 is in induction stroke for cylinder hole 50, that is, when double-head piston in Fig. 1 44 was moved to the left, the outlet 56A of passage 56 was connected to the inlet 53A of passage 53.Refrigeration agent in the passage 54 of running shaft 32 is introduced in the pressing chamber 51 in cylinder hole 50 by passage 56 and 53.
When double-head piston 44 is in discharge stroke for the first cylinder hole 50, that is, when double-head piston in Fig. 1 44 moved right, the outlet 56A of passage 56 disconnected with the inlet 53A of passage 53 and being connected.Refrigeration agent in the pressing chamber 51 is discharged in the discharge chamber 17 by exhaust port 27 when pushing expulsion valve 29 open.Being discharged to the refrigeration agent of discharging in the chamber 17 flows in the external refrigerant loop.The refrigeration agent that flows through the external refrigerant loop 38 is back to crank chamber 37 by entering the mouth then.
When compressor is in the operation and swash plate 36 during with running shaft 32 rotation, thrust bearing 46 and 47 supportings are from the thrust loads of swash plate 36.In this case, the back-up ring 63 of thrust bearing 46 not only supports thrust load but also is subjected to along the power of the sense of rotation effect of running shaft 32, makes the projection 72 of back-up ring 63 contact with 75 with holder 74 respectively with 73, thus the rotation of restriction back-up ring 63.Thereby anti-rotation mechanism 70 and 71 has prevented that the back-up ring 63 of thrust bearing 46 is with respect to cylinder body 11 rotations.
Be subjected to the restriction of the projection 72 of back-up ring 63 at the refrigeration agent stream that flows through in the 38 immediate passages 39 with inlet, make the function of this passage 39 be restricted.This has prevented to flow through and inlet 38 immediate passages 39 by the 38 refrigeration agent concentrated areas that are introduced into crank chamber 37 that enter the mouth, and makes that the amount of the refrigeration agent flow through a plurality of passages 39 is even.On the other hand, the stream that flows through the minimum passage in position 39 is subjected to the restriction of the projection 73 of back-up ring 63, makes the function limitation system of this passage 39.Make that like this lubricant oil that is stored in the crank chamber 37 is difficult to flow to suction chamber 15 by this passage 39.
Similarly, the back-up ring 66 of thrust bearing 47 not only supports thrust load but also is subjected to along the power of the sense of rotation effect of running shaft 32, makes the projection 82 of back-up ring 66 contact with 85 with holder 84 respectively with 83, thus the rotation of restriction back-up ring 66.Thereby anti-rotation mechanism 80 and 81 has prevented that the back-up ring 66 of thrust bearing 47 is with respect to cylinder body 12 rotations.
Be subjected to the restriction of the projection 82 of back-up ring 66 at the refrigeration agent stream that flows through in the 38 immediate passages 49 with inlet, make the function of this passage 49 be restricted.This has prevented to flow through and inlet 38 immediate passages 49 by the 38 refrigeration agent concentrated areas that are introduced into crank chamber 37 that enter the mouth, and makes that the amount of the refrigeration agent flow through a plurality of passages 49 is even.On the other hand, the stream that flows through in the minimum passage 49 in position is subjected to the restriction of the projection 83 of back-up ring 66, makes the function of this passage 49 be restricted.This makes the lubricant oil that is stored in the crank chamber 37 be difficult to flow to suction chamber 18 by this passage 49.
Compressor according to first mode of execution has the following advantages:
(1) anti-rotation mechanism 70,71,80,81 not only prevent thrust bearing 46,47 the back-up ring 63,66 adjacent with cylinder body 11,12 with respect to cylinder body 11,12 rotations, but also the fluid stream that flows through in the special modality 39,49 of a plurality of passages 39,49 is limited.This has prevented owing to back-up ring 63,66 rotates the wearing and tearing that produce with respect to cylinder body 11,12, and has prevented that the compressor or the performance of refrigeration circulation that cause owing to the function that limits specific passage 39,49 from reducing.
(2) amount of refrigeration agent that flows through with inlet 38 immediate passages 39,49 is tending towards bigger than the amount of the refrigeration agent of the rest channels 39,49 of far orientation than flowing through from inlet 38.Flow through the restriction that is subjected to anti-rotation mechanism 70,71,80,81 with the stream of inlet 38 immediate passages 39,49.Thereby, make that the amount of the refrigeration agent flow through a plurality of passages 39,49 is even, cause the difference of the compression efficiency in each cylinder hole less.
(3) because 70,71,80,81 pairs of anti-rotation mechanisms flow through the fluid stream of vertically observing the minimum passage in its position 39,49 and limit, the lubricant oil that therefore is stored in the lower area of crank chamber 37 is limited to flow through these passages 39,49.Thereby, having increased the amount of waiting to be stored in the lubricant oil in the crank chamber 37, the amount that causes flowing to the lubricant oil in the external refrigerant loop reduces, and prevents that the heat exchange efficiency in the refrigeration cycle from reducing.
(4) projection 72,73,82,83 that is used to limit the fluid stream that flows through special modality 39,49 of back-up ring 63,66 is subjected to holder 74,75,84,85 restrictions of cylinder body 11,12 and can't moves, thereby has prevented that back-up ring 63,66 is with respect to cylinder body 11,12 rotations.Can be only by realize that anti-Sealing shield ring 63,66 is with respect to cylinder body 11,12 rotations this simple projection 72,73,82,83 being set on the back-up ring 63,66 and holder 74,75,84,85 is set on cylinder body 11,12. Projection 72,73,82,83 restrictions are flow through the fluid stream of special modality 39,49 to limit the function of these passages 39,49.
Fig. 4 A and Fig. 4 B show second mode of execution of the present invention.The difference of second mode of execution and first mode of execution is the structure of anti-rotation mechanism.In the drawings, element common in first and second mode of executions or parts are used identical reference character, and will omit these elements of second mode of execution or the description of parts.
Shown in Fig. 4 A and Fig. 4 B, provide anti-rotation mechanism 90 by projection 92, pin 94 and passage 39.The periphery that projection 92 is formed on the back-up ring 91 adjacent with cylinder body 11 is outstanding with radially outward.Projection 92 is formed with the hole of running through wherein 93, and pin 94 is installed in the hole 93 by press fit.The diameter of pin 94 is configured to make that pin 94 is inserted in the opening of passage 39.Thrust bearing is positioned such that its back-up ring 91 is towards the end face 11B of cylinder body 11 and sell 94 and be inserted in the opening of the minimum passage in position 39.
Owing to there is the anti-rotation mechanism 90 of second mode of execution, though power is applied on the back-up ring 91 along the sense of rotation of running shaft 32 when compressor operation, but be inserted into the motion of the projection 92 of the pin 94 restriction back-up rings 91 in the opening of passage 39, thereby prevented that back-up ring 91 from rotating around axis P.Be inserted into the function that pin 94 restrictions in the opening of the minimum special modality in position 39 are flow through the fluid stream of this passage 39 and limited this passage 39.In second mode of execution, pin 94 can not be inserted in the opening of the minimum special modality in position 39 but be inserted into and the opening of the 38 immediate passages 39 that enter the mouth in.Alternately, back-up ring 91 can comprise two projections that all have pin, as projection 92 and pin 94, makes in the described pin one be inserted in the opening of the minimum passage in position 39, and another pin is inserted into and the opening of the 38 immediate passages 39 that enter the mouth in.In addition, the back-up ring that can be the thrust bearing that is close to cylinder body 12 is provided with anti-rotation mechanism, as anti-rotation mechanism 90.
According to second mode of execution, end face 11B, the 12B of cylinder body 11,12 do not need projection, and as the holder in first mode of execution 74,75,84,85, and the opening of the passage 39,49 that can be inserted pin 94 carries out freely selecting.Thereby, even when compressor during around the position change of the axis P of running shaft 32, for example when minimum passage 39,49 types according to vehicle change, the fluid stream that flows through the passage 39,49 that is positioned extreme lower position all can be restricted, and regardless of the type of vehicle.
As following illustrated, can make amendment to above-mentioned mode of execution by variety of way.
Though in the first embodiment, anti-rotation mechanism limits flowing through with immediate passage of inlet and the stream that flows through the minimum passage in position, and any passage in these two passages can be restricted.What be used for refrigeration agent is introduced that the inlet of crank chamber can be arranged on cylinder body is not the either side of bottom.First mode of execution of anti-rotation mechanism can combine with second mode of execution of anti-rotation mechanism and flow through the stream of a plurality of passages with restriction.
Though in the first embodiment, the protrusions limit of back-up ring flow through the stream of passage, thereby this projection can not allow any flow of refrigerant by closing passage.Though in the first embodiment, be provided with the gap between the opening of the projection of back-up ring and special modality, the size in gap can change according to the direction or the degree of thrust load, thereby projection is as variable throttle valve.
Though in second mode of execution, back-up ring is arranged to separate with pin, they can be set to one, and this causes the compressor number of components and parts to reduce.In addition, the cross section of pin can be Any shape, as long as this pin plays the effect that the stream of passage is flow through in restriction.Described shape for example comprises circle, polygonal and semicircle.
Though in first and second mode of executions, the present invention is applied to have the compressor that also is used as the running shaft of rotary valve, the present invention also can be applied to have the compressor of valve port plate, and wherein the valve port plate is formed with the suction port by suction valve closure.In this case, crank chamber is connected to the passage of suction chamber with acting on the main passage that compressed refrigeration agent is treated in transmission.
Claims (8)
1. fixed displacement piston type compressor comprises:
Running shaft;
Swash plate, described swash plate is fixed to described running shaft;
Cylinder body, described cylinder body supports described running shaft, and described cylinder body has a plurality of cylinders hole of arranging around described running shaft;
A plurality of pistons, described a plurality of pistons are contained in the corresponding cylinder hole, and piston is attached to described running shaft by described swash plate;
Crank chamber, the refrigeration agent with suction pressure is introduced in the described crank chamber, and described swash plate is contained in the described crank chamber;
Housing, described housing is connected to described cylinder body, and forms suction chamber and discharge the chamber in described housing;
A plurality of passages, described a plurality of passages are used for being communicated with between described crank chamber and described suction chamber;
Thrust bearing, described thrust bearing are arranged between described swash plate and the described cylinder body with the thrust load of carrying from described swash plate, and described thrust bearing has the back-up ring with the adjacent setting of described cylinder body; And
Anti-rotation mechanism, described anti-rotation mechanism are used to prevent that described back-up ring from rotating with respect to described cylinder body,
It is characterized in that described anti-rotation mechanism limits the fluid stream that flows through in the special modality in described a plurality of passages.
2. fixed displacement piston type compressor according to claim 1, wherein, described special modality is that its opening that leads to described crank chamber is positioned when compressor is installed in the vehicle that passage of viewed extreme lower position vertically.
3. fixed displacement piston type compressor according to claim 1, also comprise inlet, refrigeration agent with suction pressure is introduced in the described crank chamber by described inlet, and wherein, described special modality is that its opening that leads to described crank chamber is positioned to and immediate that passage of described inlet.
4. according to each described fixed displacement piston type compressor in the claim 1 to 3, wherein, each tunnel-shaped is formed in the described cylinder body, and the opening that leads to described crank chamber of each passage is arranged to around described back-up ring.
5. fixed displacement piston type compressor according to claim 4, wherein, described anti-rotation mechanism comprises:
Projection, described protrusion-shaped are formed in the periphery of described back-up ring to extend radially outwardly; And
Holder, described holder are formed in the described cylinder body to limit the motion of described projection, and described projection is arranged on the position of the opening top of described special modality.
6. fixed displacement piston type compressor according to claim 5 wherein, is provided with the gap between the opening of described special modality and the described projection.
7. fixed displacement piston type compressor according to claim 5, wherein, a pair of holder is formed in the described cylinder body with outstanding to described swash plate, and when when the sense of rotation of described running shaft is observed, the opposite side that described holder is positioned described projection makes described projection contact with described holder.
8. fixed displacement piston type compressor according to claim 4, wherein, described anti-rotation mechanism comprises:
Projection, described protrusion-shaped are formed in the periphery of described back-up ring to extend radially outwardly; And
Pin, described pin is mounted to described projection, and described pin inserts in the described opening of described special modality.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009114169A JP2010261406A (en) | 2009-05-11 | 2009-05-11 | Fixed displacement piston compressor |
| JP2009-114169 | 2009-05-11 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101886623A true CN101886623A (en) | 2010-11-17 |
Family
ID=43061571
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010101739046A Pending CN101886623A (en) | 2009-05-11 | 2010-05-07 | Fixed displacement piston type compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20100282070A1 (en) |
| JP (1) | JP2010261406A (en) |
| KR (1) | KR101121945B1 (en) |
| CN (1) | CN101886623A (en) |
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|---|---|---|---|---|
| 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 |
| CN108005876A (en) * | 2016-11-02 | 2018-05-08 | 现代自动车株式会社 | Compressor of air conditioner for vehicle |
| CN108827785A (en) * | 2018-05-03 | 2018-11-16 | 辽宁工程技术大学 | A kind of three axis loading device of coal seam containing gas constant volume |
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| US10309380B2 (en) | 2011-11-16 | 2019-06-04 | Ocean Pacific Technologies | Rotary axial piston pump |
| US10094364B2 (en) | 2015-03-24 | 2018-10-09 | Ocean Pacific Technologies | Banded ceramic valve and/or port plate |
| CN110891541A (en) | 2017-05-05 | 2020-03-17 | 巴德里·阿穆图尔 | Stimulation method and apparatus |
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| US20020117050A1 (en) * | 2001-02-23 | 2002-08-29 | Halla Climate Control Corporation | Swash plate compressor |
| CN1495358A (en) * | 2002-08-30 | 2004-05-12 | ��ʽ��������Զ�֯�������� | Rotary sloping tray type positive displacement compuessor |
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| US4974702A (en) * | 1989-01-27 | 1990-12-04 | Kabushiki Kaisha Tyoda Jidoshokki Seisakusho | Swash plate type compressor with thrust bearing lubricator |
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| US5596920A (en) * | 1994-04-06 | 1997-01-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor |
| JP2937040B2 (en) * | 1994-11-18 | 1999-08-23 | 株式会社豊田自動織機製作所 | Double head swash plate type compressor |
| JPH08144945A (en) * | 1994-11-22 | 1996-06-04 | Toyota Autom Loom Works Ltd | Double head cam plate type compressor |
| JPH08261147A (en) * | 1995-03-20 | 1996-10-08 | Toyota Autom Loom Works Ltd | Reciprocating piston type compressor |
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| JP4946340B2 (en) * | 2005-10-17 | 2012-06-06 | 株式会社豊田自動織機 | Double-head piston compressor |
| KR101159863B1 (en) * | 2006-07-24 | 2012-06-25 | 한라공조주식회사 | Compressor |
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2010
- 2010-04-21 KR KR1020100036825A patent/KR101121945B1/en not_active IP Right Cessation
- 2010-04-28 US US12/769,047 patent/US20100282070A1/en not_active Abandoned
- 2010-05-07 CN CN2010101739046A patent/CN101886623A/en active Pending
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| US4990064A (en) * | 1988-08-08 | 1991-02-05 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Multi-piston swash plate type compressor with internal lubricating arrangement |
| CN1162700A (en) * | 1996-02-20 | 1997-10-22 | 株式会社丰田自动织机制作所 | Variable capacity refrigerant compressor |
| CN1276495A (en) * | 1999-06-07 | 2000-12-13 | 株式会社丰田自动织机制作所 | Variable displacement compressor with one-way valve |
| US20010008607A1 (en) * | 2000-01-19 | 2001-07-19 | Toshiro Fujii | Swash plate type compressor |
| US20020117050A1 (en) * | 2001-02-23 | 2002-08-29 | Halla Climate Control Corporation | Swash plate compressor |
| CN1495358A (en) * | 2002-08-30 | 2004-05-12 | ��ʽ��������Զ�֯�������� | Rotary sloping tray type positive displacement compuessor |
Cited By (5)
| 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 |
| CN108005876A (en) * | 2016-11-02 | 2018-05-08 | 现代自动车株式会社 | Compressor of air conditioner for vehicle |
| CN108005876B (en) * | 2016-11-02 | 2021-03-05 | 现代自动车株式会社 | Air conditioner compressor for vehicle |
| CN108827785A (en) * | 2018-05-03 | 2018-11-16 | 辽宁工程技术大学 | A kind of three axis loading device of coal seam containing gas constant volume |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2010261406A (en) | 2010-11-18 |
| KR20100122055A (en) | 2010-11-19 |
| US20100282070A1 (en) | 2010-11-11 |
| KR101121945B1 (en) | 2012-03-09 |
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Application publication date: 20101117 |