CN105556121A - Variable-capacity swash plate compressor - Google Patents

Variable-capacity swash plate compressor Download PDF

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Publication number
CN105556121A
CN105556121A CN201480050320.6A CN201480050320A CN105556121A CN 105556121 A CN105556121 A CN 105556121A CN 201480050320 A CN201480050320 A CN 201480050320A CN 105556121 A CN105556121 A CN 105556121A
Authority
CN
China
Prior art keywords
swash plate
compressor
inclination
angle
chamber
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.)
Granted
Application number
CN201480050320.6A
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Chinese (zh)
Other versions
CN105556121B (en
Inventor
山本真也
山崎佑介
铃木隆容
本田和也
太田雅树
仲井间裕之
山下秀晴
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Toyota Industries Corp
Original Assignee
Toyoda Automatic Loom Works Ltd
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Filing date
Publication date
Application filed by Toyoda Automatic Loom Works Ltd filed Critical Toyoda Automatic Loom Works Ltd
Publication of CN105556121A publication Critical patent/CN105556121A/en
Application granted granted Critical
Publication of CN105556121B publication Critical patent/CN105556121B/en
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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
    • F04B27/1072—Pivot mechanisms
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • 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
    • F04B27/1009—Distribution members
    • 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
    • F04B27/1045—Cylinders
    • 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
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

Provided is a variable-capacity swash plate compressor that exhibits superior mountability and high controllability. The compressor is provided with an actuator (13). The actuator (13) has a mobile body (13a) and a control pressure chamber (13b). The mobile body (13) has a first mobile tube (131), and an action section (134) is provided in a protruding manner to the back end of the first mobile tube (131). A planar action surface (134a) is formed at the action section (134). Also, a convex section (5g) is formed at the swash plate main body (50) of the swash plate (5) in the compressor. The convex section (5g) is positioned at the side of a section (T) corresponding to the top dead center of the swash plate (5) in the front surface (5a) of the swash plate main body (50). In the compressor, the action surface (134a) and the convex section (5g) contact at an action position (F). Thus, the action position (F) moves towards the drive shaft center (O) side when the inclination angle of the swash plate (5) becomes small.

Description

Capacity variable type tilted-plate compressor
Technical field
The present invention relates to capacity variable type tilted-plate compressor.
Background technique
Patent Document 1 discloses existing capacity variable type tilted-plate compressor (hereinafter referred to as compressor.)。This compressor possesses housing, live axle, swash plate, linkage mechanism, multiple piston, switching mechanism and capacity control mechanism.
Suction chamber, discharge chamber, swash plate room and multiple cylinder holes is formed at housing.Live axle can be supported on housing rotatably.Swash plate can by the rotation of live axle in the indoor rotation of swash plate.Linkage mechanism is arranged between live axle and swash plate, the change at the angle of inclination in its direction allowing swash plate orthogonal relative to the driving axle center with live axle.This linkage mechanism has protruding part and transferring elements.Protruding part is fixed on live axle in swash plate indoor.Transferring elements is arranged with swash plate integratedly in swash plate indoor, and the rotation of protruding part is passed to swash plate.Each piston can reciprocatingly be accommodated in each cylinder holes respectively.Switching mechanism is by the rotation of swash plate thus with the stroke corresponding with angle of inclination, each piston is moved back and forth in each cylinder holes.Capacity control mechanism has air feed path, bleed path and control valve.Discharge chamber is communicated with swash plate room by air feed path.Swash plate room is communicated with suction chamber by path of bleeding.Control valve by the aperture of adjustment air feed path, thus can change the pressure of swash plate indoor.
In this compressor, if utilize control valve to make the pressure of swash plate indoor for high pressure, then angle of inclination diminishes, thus the stroke of piston reduces.Therefore, each compression volume turned of live axle diminishes.On the other hand, if utilize control valve to make the pressure of swash plate indoor for low pressure, then the angle of inclination of swash plate becomes large, thus the stroke of piston increases.Therefore, each compression volume turned of live axle becomes large.Like this, in this compressor, the discharge capacity of refrigeration agent can be changed according to the operational situation of carried vehicle etc.
But, as this compressor, when angle of inclination is changed in the pressure change by swash plate indoor, need the refrigeration agent of guaranteeing to be enough to the amount changing angle of inclination in swash plate indoor.Therefore, compressor easily maximizes because of larger swash plate room.
In addition, in this compressor, the blow-by gas of high pressure is inevitable towards the inflow of swash plate indoor.In addition, in this compressor, the easily condensation thus produce hydrops in swash plate room because of the reduction of outside air temperature of the refrigeration agent of swash plate indoor.Therefore, in this compressor, be difficult to suitably change angle of inclination.
Therefore, it is also proposed compressor such disclosed in patent documentation 2.This compressor possesses the actuator that can change angle of inclination and the control mechanism controlled actuator.
Specifically, actuator has: protruding part; Movable body, it can integrally rotatably engage with swash plate, and can move along driving axis direction and change angle of inclination; And control pressure chamber, it is divided by protruding part and movable body, and by the pressure of inside, movable body is moved.Control mechanism has control access and control valve.Control access has: transformation path, and it is communicated with control pressure chamber; Low-pressure passage, it is communicated with suction chamber and swash plate room; And high-pressure passage, it is communicated with discharge chamber.A part for transformation path is formed in live axle.The aperture of control valve adjustment transformation path, low-pressure passage and high-pressure passage.That is, transformation path is communicated with low-pressure passage or high-pressure passage by control valve.
In this compressor, if transformation path is communicated with high-pressure passage by control valve, then control to become high pressure in pressure chamber compared with swash plate room.Thus, the movable body of actuator is away from protruding part, thus angle of inclination is reduced.Therefore, the stroke of piston reduces, and discharge capacity diminishes.On the other hand, if transformation path is communicated with low-pressure passage by control valve, then control to become the low pressure with swash plate room same degree in pressure chamber.Thus, the movable body of actuator is close to protruding part, thus angle of inclination becomes large.Therefore, the stroke of piston increases, and capacity of discharging becomes large.
In this compressor, owing to carrying out the pressure change in the little control pressure chamber in volume ratio swash plate room, so compared with the compressor changed with the pressure carrying out swash plate indoor, the amount of the refrigeration agent needed for change at angle of inclination can be reduced, thus can realize miniaturization.
In addition, in this compressor, because angle of inclination is changed in the pressure change by controlling pressure chamber, so blow-by gas is difficult to bring negative effect to the change at angle of inclination towards the hydrops of the inflow of swash plate indoor, swash plate indoor.
Patent documentation 1: Japanese Unexamined Patent Publication 2002-213350 publication
Patent documentation 2: Japanese Laid-Open Patent Publication 52 ?No. 131204 publications
But in the compressor described in above-mentioned patent documentation 2, movable body and the swash plate of actuator are orthogonal to by the corresponding portion of the top dead center defined at swash plate and the first imaginary plane driving axle center to determine, and engage on the second imaginary plane comprising driving axle center.More specifically, movable body engages by having the hinged ball at center in the heart at live axle with swash plate.And, the working position that movable body is abutted with hinged ball along with the change at the angle of inclination of swash plate with the parallel to an axis of live axle change.In addition, make hinged ball also identical with the working position that swash plate abuts.That is, in this compressor, even if the angle of inclination of swash plate changes, working position does not also change with driving the distance in axle center.
Therefore, in this compressor, when reducing angle of inclination, need increase swash plate room and control the differential pressure of pressure chamber (hereinafter referred to as variable differential pressure.) thus utilize larger thrust that movable body is moved.That is, in this compressor, the load of movable body during reduction angle of inclination is larger.Therefore, in this compressor, the variable quantity of variable differential pressure during change angle of inclination is comparatively large, is difficult to promptly change angle of inclination according to the operational situation of vehicle etc., thus causes controlling to reduce.
In addition, in this compressor, because working position does not change with driving the distance in axle center, so when changing the angle of inclination of swash plate, the stroke of the driving axis direction of movable body is larger.Therefore, in this compressor, cannot major axis be avoided, therefore worry the lift-launch for vehicle etc.
Summary of the invention
The present invention proposes in view of above-mentioned existing actual conditions, for the problem solved, it is that providing a kind of can either play the capacity variable type tilted-plate compressor that higher controlling can play again excellent lift-launch.
The feature of capacity variable type tilted-plate compressor of the present invention is to possess: housing, and it is formed with swash plate room and cylinder holes; Live axle, it can be supported on above-mentioned housing rotatably; Swash plate, it can by the rotation of above-mentioned live axle in the indoor rotation of above-mentioned swash plate; Linkage mechanism, it is arranged between above-mentioned live axle and above-mentioned swash plate, and the change at the angle of inclination in the direction allowing above-mentioned swash plate orthogonal relative to the driving axle center with above-mentioned live axle; Piston, it can reciprocatingly be accommodated in above-mentioned cylinder holes; Switching mechanism, its rotation by above-mentioned swash plate and above-mentioned piston is moved back and forth in above-mentioned cylinder holes with the stroke corresponding with above-mentioned angle of inclination; Actuator, it can change above-mentioned angle of inclination; And control mechanism, it controls above-mentioned actuator,
Aforementioned link mechanism has: protruding part, and it is fixed on above-mentioned live axle in above-mentioned swash plate indoor; And transferring elements, the rotation of above-mentioned protruding part is passed to above-mentioned swash plate by it,
Above-mentioned actuator has: above-mentioned protruding part; Movable body, it can rotate integrally with above-mentioned swash plate, and can move along above-mentioned driving axis direction thus change above-mentioned angle of inclination; And control pressure chamber, it is divided by above-mentioned protruding part and above-mentioned movable body, and changes inner pressure by above-mentioned control mechanism thus above-mentioned movable body is moved,
Being formed at above-mentioned movable body can by the pressure in above-mentioned control pressure chamber to press the service portion of above-mentioned swash plate,
Be formed at above-mentioned swash plate and abut with above-mentioned service portion and the portion that is applied be pressed,
Above-mentioned service portion abuts at working position with the above-mentioned portion that is applied,
Above-mentioned working position is moved by the change at above-mentioned angle of inclination,
The top dead center correspondence portion making above-mentioned piston be positioned at top dead center is had in above-mentioned swash plate definition,
Compared with above-mentioned working position when being minimum with above-mentioned angle of inclination, above-mentioned working position when above-mentioned angle of inclination is maximum is closer to above-mentioned top dead center correspondence portion.
In compressor of the present invention, the rotation of protruding part is passed to swash plate by the transferring elements of linkage mechanism.And the working position making the service portion of movable body abut with the portion of being applied of swash plate is moved by the change at the angle of inclination of swash plate.Specifically, compared with working position when being minimum with angle of inclination, working position when angle of inclination is maximum is closer to the top dead center correspondence portion of swash plate.
Therefore, in this compressor, even if compared with the situation that angle of inclination changes, working position is also constant with the distance in driving axle center of the swash plate when reducing angle of inclination, even if do not increase variable differential pressure to guarantee larger thrust, movable body also can be made to move.That is, in this compressor, the load of movable body when angle of inclination is diminished can be reduced.Therefore, in this compressor, the variable quantity of variable differential pressure during change angle of inclination is less, easily promptly changes angle of inclination according to the operational situation of vehicle etc., thus can play higher controlling.
In addition, in this compressor, because working position is moved by the change at the angle of inclination of swash plate as described above, so when range of tilt angles is identical, the stroke of the driving axis direction of movable body can be reduced.Thus, in this compressor, the maximization of axial length can be suppressed.
Therefore, compressor of the present invention can either play higher controlling and can play excellent lift-launch again.
In addition, such as, the structure linked with the portion of being applied by service portion by connection pin etc. can not be adopted.But, in this case, there is the worry posture of movable body being changed because of the structure of linking portion.In addition, also can make the complex structure of compressor because of the increase of parts number of packages, and manufacture cost is increased.On the other hand, in compressor of the present invention, when the change at angle of inclination carrying out swash plate, only make movable body directly abut with swash plate and press it, thus the posture of movable body is difficult to change.In addition, in this compressor, the complicated of structure can be suppressed, thus cheapization of manufacture cost can be realized.
Control mechanism can have control access and control valve.Control access can have the transformation path, the low-pressure passage be communicated with suction chamber or swash plate room and the high-pressure passage be communicated with discharge chamber that are communicated with control pressure chamber.
Preferred movable body is inserted for live axle and can be chimeric with protruding part.In this case, between protruding part and swash plate, suitably can guarantee the space for driving axis direction movement for movable body edge.
In addition, movable body can have the movable cylinders portion be formed as with the cylindrical shape driving axle center coaxial.And preferably, protruding part has cylindric stationary cylinder portion, and the stationary cylinder portion of this cylindrical shape is formed as and the cylindrical shape driving axle center coaxial at the outer circumferential side in movable cylinders portion, and guarantee to control pressure chamber in movable cylinders portion.In this case, by movable cylinders portion is chimeric with stationary cylinder portion, thus movable body can be made chimeric with protruding part.In addition, guarantee in movable cylinders portion owing to utilizing stationary cylinder portion to control pressure chamber, thus can between protruding part and movable body suitably formation control pressure chamber.
In addition, in this case, the first sealing component to controlling pressure chamber and sealing can be provided with between movable cylinders portion and live axle.And, preferably, between movable cylinders portion and stationary cylinder portion, be provided with the second sealing component to controlling pressure chamber and sealing.Thereby, it is possible to suitably guarantee the tightness controlling pressure chamber.In addition, as the first sealing component and the second sealing component, except O type ring etc., also various Sealing can be adopted.In addition, the first sealing component and the second sealing component can be same, also can be different.
The thrust-bearing bearing the thrust acting on piston can be provided with between housing and protruding part.And preferably, it is little and can be fitted in thrust-bearing that movable cylinders portion is formed as diameter specific thrust bearing.
In this case, utilize thrust-bearing, when acting on suction reaction force, the compression stroke of piston when suitably can support suction stroke, act on the compression reaction force of piston.In addition, because movable cylinders portion can be fitted in thrust-bearing, even if thus the axial length of compressor is shorter, also can guarantee fully for for movable body along the space driving axis direction movement.
In addition, in compressor of the present invention, preferably, service portion be applied portion at the mutual point cantact of working position or linear contact lay.In this case, service portion and the area of contact being applied portion can be reduced.In addition, the straight line of linear contact lay is relative to orthogonal with the first imaginary plane driving axle center to determine by the top dead center correspondence portion of swash plate.In addition, preferably, when making service portion at working position and being applied portion's point cantact or linear contact lay, service portion be applied portion abutting portion or be applied portion squarely become curved surface with one of the abutting portion of service portion.
In addition, the position forming service portion on movable body, the position forming the portion that is applied on swash plate can suitably be designed.Particularly, in compressor of the present invention, service portion and the portion that is applied can from the driving axle center upwards stop correspondence portion lateral deviation hearts.And preferably, if angle of inclination diminishes, then working position moves to driving side, axle center.
In this case, the change at angle of inclination can not be hindered, between protruding part and swash plate, easily guarantee the space for driving axis direction movement for movable body edge.Therefore, in this compressor, the maximization of axial length can either be suppressed, the large footpath of actuator can be made again, thus can utilize enough thrust that movable body is promptly moved.
Service portion can have the acting surface extended along the direction orthogonal with driving axle center.And preferably, the portion of being applied has gives prominence to and the protuberance abutted with acting surface from swash plate.In this case, service portion and the portion's of being applied suitably point cantact or linear contact lay can be made.
Preferably, service portion is arranged at the side, top dead center correspondence portion in movable cylinders portion highlightedly.In this case, service portion can be made easily to abut with the portion of being applied.
Preferably, swash plate has: swash plate main body, and it is formed with the inserting hole passed for live axle; And being applied portion, it is integrally formed in swash plate main body.In this case, the minimizing of the parts number of packages of compressor can be realized, thus easily carry out manufacturing the minimizing that also can realize manufacture cost.
In addition, also preferably swash plate has: swash plate main body, and it is formed with the inserting hole passed for live axle; And being applied portion, it is fixed on swash plate main body.In this case, swash plate main body can be improved, be applied the degrees of freedom of the design in portion.
In compressor of the present invention, suction chamber and discharge chamber can be formed with at housing.And preferably, suction chamber is communicated with swash plate room.In this case, can make swash plate room in the same manner as suction chamber is low pressure.
In addition, control mechanism can have: control access, and it will control pressure chamber and be communicated with suction chamber and/or discharge chamber; And control valve, it can adjust the aperture of control access.And, preferably, control access be formed in live axle at least partially.In this case, control mechanism miniaturization can either be made, again can pressure suitably in Variation control pressure chamber, thus movable body can be made suitably to move.
Can be formed with pressure control chamber between housing and one end of live axle, this pressure control chamber is communicated with via control access with control pressure chamber and changes pressure by control valve.And, preferably, between housing and live axle, be provided with the 3rd sealing component that pressure control chamber is sealed.
In this case, utilize control valve to change the pressure of pressure control chamber, thus control pressure chamber make movable body move.And, utilize the 3rd sealing component suitably can guarantee the tightness of pressure control chamber.In addition, the 3rd sealing component is identical with first, second sealing component above-mentioned, except O type ring etc., also can adopt various Sealing.In addition, the 3rd sealing component can be same with first, second sealing component, also can be different.
Compressor of the present invention can either play higher controlling can play excellent lift-launch again.
Accompanying drawing explanation
Sectional view when Fig. 1 is the maximum capacity of the compressor of embodiment 1.
Fig. 2 relates to the compressor of embodiment 1, is the schematic diagram representing control mechanism.
Fig. 3 relates to the compressor of embodiment 1, is the major component amplification view of the rear end part representing live axle.
Fig. 4 relates to the compressor of embodiment 1, is the major component amplification view representing actuator.
Fig. 5 relates to the compressor of embodiment 1, is the stereogram from forward observation representing swash plate.
Sectional view when Fig. 6 is the minimum capacity of the compressor of embodiment 1.
Fig. 7 relates to the compressor of embodiment 1, it is the major component amplification view representing service portion Yu be applied portion, (A) working position of angle of inclination when being maximum is represented, working position when (B) represents that angle of inclination is minimum.
Fig. 8 is the coordinate diagram of the relation representing angle of inclination and variable differential pressure.
Fig. 9 is the different schematic diagram of the stroke of the movable body represented in the compressor of embodiment 1 and the compressor of comparative example.
Sectional view when Figure 10 is the maximum capacity of the compressor of embodiment 2.
Embodiment
Below, with reference to accompanying drawing, the embodiment 1,2 the present invention specialized is described.The compressor of embodiment 1,2 is capacity variable type single head tilted-plate compressors.Above-mentioned compressor is all equipped on vehicle, forms the refrigerating circuit of air conditioner for vehicles.
(embodiment 1)
As shown in Figure 1, the compressor of embodiment 1 possesses: housing 1; Live axle 3; Swash plate 5; Linkage mechanism 7; Multiple piston 9; Multipair crawler shoe 11a, 11b; Actuator 13; And the control mechanism 15 shown in Fig. 2.In addition, for the ease of being described, the shape of swash plate 5 being simplified illustrate in FIG.Also identical about Fig. 6, Figure 10 described later.
As shown in Figure 1, housing 1 has: the front case 17 being positioned at the front of compressor; Be positioned at the rear case 19 at the rear of compressor; Cylinder body 21 between front case 17 and rear case 19; And valve cell 23.
Front case 17 has: in front along the antetheca 17a that the above-below direction of compressor extends; And form as one and the perisporium 17b extended towards rear from the front of compressor with antetheca 17a.Front case 17 utilizes above-mentioned antetheca 17a and perisporium 17b and is formed as approximate cylinder shape with the end.In addition, utilize above-mentioned antetheca 17a and perisporium 17b, thus be formed with swash plate room 25 in front case 17.
Flange 17c outstanding is toward the front formed at antetheca 17a.Gland seal device 27 is provided with in this flange 17c.In addition, in flange 17c, be formed with the first axis hole 17d that the fore-and-aft direction along compressor extends.The first sliding bearing 29a is provided with in this first axis hole 17d.
The suction port 250 be communicated with swash plate room 25 is formed at perisporium 17b.Swash plate room 25 is connected with not shown vaporizer by this suction port 250.
A part for control mechanism 15 is provided with at rear case 19.In addition, the first pressure control chamber 31a, suction chamber 33 and discharge chamber 35 is formed with at rear case 19.First pressure control chamber 31a is positioned at the core of rear case 19.Discharge chamber 35 is annularly positioned at the outer circumferential side of rear case 19.In addition, suction chamber 33 is formed as ring-type at rear case 19 between the first pressure control chamber 31a and discharge chamber 35.Discharge chamber 35 is connected with not shown exhaust port.
At cylinder body 21, circumferentially equiangularly gap-forming has the cylinder holes 21a with piston 9 same number.The forward end of each cylinder holes 21a is communicated with swash plate room 25.In addition, at cylinder body 21, be formed with the retaining groove 21b that the lift amount of aftermentioned inhalation reed valve 41a is limited.
Further, at cylinder body 21, throughly the second axis hole 21c being not only communicated with swash plate room 25 but also extending along the fore-and-aft direction of compressor is provided with.The second sliding bearing 29b is provided with in the second axis hole 21c.In addition, spring housing 21d is formed with at cylinder body 21.This spring housing 21d is between swash plate room 25 and the second axis hole 21c.Return spring 37 is configured with in spring housing 21d.To be minimum swash plate 5 by angle of inclination exert a force towards the front of swash plate room 25 this return spring 37.In addition, the suction passage 39 be communicated with swash plate room 25 is formed at cylinder body 21.
Valve cell 23 is arranged between rear case 19 and cylinder body 21.This valve cell 23 comprises valve plate 40, sucks valve plate 41, discharges valve plate 43 and baffle plate 45.
At valve plate 40, discharge valve plate 43 and baffle plate 45, be formed with the suction port 40a of number identical with cylinder holes 21a.In addition, at valve plate 40 and suction valve plate 41, the exhaust port 40b of number identical with cylinder holes 21a is formed with.Each cylinder holes 21a is communicated with suction chamber 33 by each suction port 40a, and is communicated with discharge chamber 35 by each exhaust port 40b.Further, at valve plate 40, suck valve plate 41, discharge valve plate 43 and baffle plate 45, be formed with the first intercommunicating pore 40c and the second intercommunicating pore 40d.Suction chamber 33 is communicated with by the first intercommunicating pore 40c with suction passage 39.
Suck the front surface that valve plate 41 is arranged at valve plate 40.At this suction valve plate 41, be formed with multiple inhalation reed valve 41a that can be carried out opening and closing by resiliently deformable to each suction port 40a.In addition, the rear surface that valve plate 43 is arranged at valve plate 40 is discharged.At this discharge valve plate 43, be formed with multiple discharge leaf valve 43a that can be carried out opening and closing by resiliently deformable to each exhaust port 40b.Baffle plate 45 is arranged at the rear surface of discharging valve plate 43.The lift amount of leaf valve 43a is discharged in the restriction of this baffle plate 45.
Live axle 3 is inserted from flange 17c side towards the rear side of housing 1.The forward end of live axle 3 is supported by gland seal device 27 axle in flange 17c, and is supported by the first sliding bearing 29a axle in the first axis hole 17d.In addition, the rear end side of live axle 3 is supported by the second sliding bearing 29b axle in the second axis hole 21c.Like this, live axle 3 is can be supported on housing 1 around the mode driving axle center O to rotate.And, divide in the second axis hole 21c and between the rear end of live axle 3 and have the second pressure control chamber 31b.This second pressure control chamber 31b is communicated with the first pressure control chamber 31a by the second intercommunicating pore 40d.Pressure control chamber 31 is formed by first, second pressure control chamber 31a, 31b.
As shown in Figure 3, circular groove 3c, 3d is formed with in the rear end of live axle 3.O type ring 49a, 49b is respectively arranged with at each circular groove 3c, 3d.Pressure control chamber 31 is sealed by each O type ring 49a, 49b, thus swash plate room 25 is not communicated with pressure control chamber 31.Above-mentioned each O type ring 49a, 49b are equivalent to the 3rd sealing component of the present invention.
As shown in Figure 1, at live axle 3, linkage mechanism 7, swash plate 5 and actuator 13 are installed.Linkage mechanism 7 comprises flange 51, is formed at a pair male arms 53 of flange 51 and a pair swash plate arm 5e, 5f.Flange 51 is equivalent to protruding part of the present invention.In addition, swash plate arm 5e, 5f are equivalent to transferring elements of the present invention.
Flange 51 is formed as approximate circle ring-type.This flange 51 is pressed into live axle 3, and can rotate integratedly with live axle 3.This flange 51 is positioned at the forward end of swash plate room 25, and is configured at than swash plate 5 position on the front.In addition, between flange 51 and antetheca 17a, thrust-bearing 55 is provided with.
As shown in Figure 4, the stationary cylinder portion 51a of the cylindrical shape that the fore-and-aft direction along flange 51 extends is arranged with at flange 51.As shown in Figure 1, this stationary cylinder portion 51a extends to the position of the inner side being in thrust-bearing 55 in flange 51 from the ear end face of flange 51.
Each male arms 53 extends from flange 51 towards rear.In addition, the position at flange 51 and between each male arms 53 is formed with camming surface 51b.In addition, for convenience of explanation, in Fig. 1 etc., only illustrate the side of male arms 53.
As shown in Figure 5, swash plate 5 has swash plate main body 50, swash plate arm 5e, 5f and protuberance 5g.This protuberance 5g is equivalent to of the present inventionly be applied portion.
Swash plate main body 50 writing board shape in the form of a ring, it is except having front surface 5a and rear surface 5b, and also definition has the top dead center correspondence portion T making each piston 9 be positioned at top dead center.In addition, the limiting unit 5c outstanding towards the front of swash plate 5 is formed with at front surface 5a.As shown in Figure 1, this limiting unit 5c abuts with flange 51 when the angle of inclination of swash plate 5 becomes maximum.In addition, inserting hole 5d is formed with in swash plate main body 50.Live axle 3 has been inserted at this inserting hole 5d.
As shown in Figure 5, each swash plate arm 5e, 5f, at the front surface 5a of swash plate main body 50, are formed at the position from driving axle center O to the top dead center correspondence portion T lateral deviation heart of swash plate 5.Each swash plate arm 5e, 5f extend toward the front from front surface 5a.
Protuberance 5g is arranged toward the front highlightedly from front surface 5a, and forms as one with swash plate main body 50.This protuberance 5g is formed as approximate hemispherical, its from drive the top dead center correspondence portion T lateral deviation heart from axle center O to swash plate 5 and between swash plate arm 5e and swash plate arm 5f.
As shown in Figure 1, by swash plate arm 5e, 5f being inserted between each male arms 53, thus flange 51 and swash plate 5 are linked.Thus, swash plate 5 can rotate together with flange 51 in swash plate room 25.Each forward end of each swash plate arm 5e, 5f abuts with camming surface 51b respectively.
In addition, because flange 51 and swash plate 5 link, thus each swash plate arm 5e, 5f and protuberance 5g is positioned at the position from driving axle center O to the top dead center correspondence portion T lateral deviation heart of swash plate 5.And, because swash plate arm 5e, 5f slide at camming surface 51b, thus swash plate 5 for self relative to the angle of inclination driving the orthogonal direction of axle center O, can roughly maintain the position of top dead center correspondence portion T, while change to the minimum cant shown in Fig. 6 from the maximum tilt angle shown in this figure in limit.
As shown in Figure 4, actuator 13 comprises flange 51, movable body 13a and controls pressure chamber 13b.
Movable body 13a driven shaft 3 is inserted, and can limit and O direction, driving axle center, live axle 3 sliding contact edge move.This movable body 13a is formed as the cylindrical shape coaxial with live axle 3, and is formed as the diameter less than the thrust-bearing 55 shown in Fig. 1.As shown in Figure 4, movable body 13a has the first movable cylinders portion 132 of movable cylinders portion 131, second and the 3rd movable cylinders portion 133.First movable cylinders portion 131 is positioned at the rear end side of movable body 13a, and it is formed as minimum diameter in movable body 13a.The front end in the second movable cylinders portion 132 and the first movable cylinders portion 131 is continuous, and is formed as diameter and expands gradually towards the front of movable body 13a.The front end in the 3rd movable cylinders portion 133 and the second movable cylinders portion 132 is continuous, and extends towards the front of movable body 13a.3rd movable cylinders portion 133 is formed as maximum diameter in movable body 13a.
In addition, service portion 134 is integrally formed with in the rear end in the first movable cylinders portion 131.As shown in Figure 1, service portion 134 vertically extends from the T side, top dead center correspondence portion driving O side, axle center towards swash plate 5, and from the top dead center correspondence portion T lateral deviation heart driving axle center O to swash plate 5.This service portion 134 has the acting surface 134a being formed as plane.As shown in Figure 8, acting surface 134a is at working position F and protuberance 5g point cantact.Thus, movable body 13a can rotate integrally with flange 51 and swash plate 5.Here, because protuberance 5g and service portion 134 are from the top dead center correspondence portion T lateral deviation heart driving axle center O to swash plate 5, so as shown in Figure 1, working position F is also from the top dead center correspondence portion T lateral deviation heart driving axle center O to swash plate 5.
Movable body 13a enters in stationary cylinder portion 51a by making the second movable cylinders portion 132 shown in Fig. 4 and the 3rd movable cylinders portion 133, thus can chimeric with flange 51 (with reference to Fig. 1).And under the second movable cylinders portion 132 and the 3rd movable cylinders portion 133 enter the darkest state of stationary cylinder portion 51a, the 3rd movable cylinders portion 133 arrives the position of the inner side of thrust-bearing 55 in stationary cylinder portion 51a.
As shown in Figure 4, control pressure chamber 13b to be formed between the second movable cylinders portion 132, the 3rd movable cylinders portion 133, stationary cylinder portion 51a and live axle 3.In addition, be formed with circular groove 131a at the inner peripheral surface in the first movable cylinders portion 131, be formed with circular groove 133a at the outer circumferential face in the 3rd movable cylinders portion 133.O type ring 49c, 49d is respectively arranged with at above-mentioned each circular groove 131a, 133a.This O type ring 49c is equivalent to the first sealing component of the present invention, and O type ring 49d is equivalent to the second sealing component of the present invention.Utilize above-mentioned O type ring 49c, 49d to seal and control pressure chamber 13b, thus guarantee to control the tightness in pressure chamber 13b.
As shown in Figure 1, be formed in live axle 3: drive the axle road 3a that O direction, axle center extends from the rear end of live axle 3 towards front end edge; And extend and the pathway 3b opened at the outer circumferential face of live axle 3 from the front end edge radial direction of axle road 3a.The rear end of axle road 3a is opened in pressure control chamber 31.On the other hand, pathway 3b opens at control pressure chamber 13b.Pressure control chamber 31 is communicated with by above-mentioned axle road 3a and pathway 3b with control pressure chamber 13b.
Live axle 3 is connected with not shown belt wheel or magnetic clutch by being formed at the screw section 3e of front end.
Each piston 9 is accommodated in each cylinder holes 21a respectively, and can move back and forth in each cylinder holes 21a.Utilize above-mentioned each piston 9 with valve cell 23 thus divide pressing chamber 57 in each cylinder holes 21a.
In addition, engagement portion 9a is arranged with respectively at each piston 9.Hemispheric crawler shoe 11a, 11b is respectively arranged with in the 9a of this engagement portion.The rotation of swash plate 5 is converted to moving back and forth of each piston 9 by each crawler shoe 11a, 11b.Above-mentioned each crawler shoe 11a, 11b are equivalent to switching mechanism of the present invention.Like this, each piston 9 can move back and forth respectively with the stroke corresponding with the angle of inclination of swash plate 5 in cylinder holes 21a.In addition, except crawler shoe 11a, 11b, also can to adopt in the 5b side, rear surface of swash plate main body 50 the supporting oscillation plate via thrust-bearing and utilize the swing type switching mechanism that wobble plate is connected with each piston 9 by connecting rod.
As shown in Figure 2, control mechanism 15 has low-pressure passage 15a, high-pressure passage 15b, control valve 15c, throttle orifice 15d, axle road 3a and pathway 3b.Control access of the present invention is formed by above-mentioned low-pressure passage 15a, high-pressure passage 15b, axle road 3a and pathway 3b.In addition, axle road 3a and pathway 3b plays function as transformation path.
Low-pressure passage 15a is connected with pressure control chamber 31 and suction chamber 33.Thus, control pressure chamber 13b, pressure control chamber 31 and suction chamber 33 and become by this low-pressure passage 15a, axle road 3a and pathway 3b the state be interconnected.High-pressure passage 15b is connected with pressure control chamber 31 and discharge chamber 35.Control pressure chamber 13b, pressure control chamber 31 and discharge chamber 35 to be communicated with by this high-pressure passage 15b, axle road 3a and pathway 3b.In addition, high-pressure passage 15b is provided with throttle orifice 15d, thus throttling is carried out to the flow of the refrigeration agent circulated in high-pressure passage 15b.
Control valve 15c is arranged at low-pressure passage 15a.This control valve 15c can adjust based on the flow of the pressure in suction chamber 33 to the refrigeration agent circulated at low-pressure passage 15a.
In this compressor, be connected with relative to the suction port 250 shown in Fig. 1 the pipe arrangement be connected with vaporizer, and be connected with the pipe arrangement be connected with condenser relative to exhaust port.Condenser is connected with vaporizer via pipe arrangement and expansion valve.The refrigerating circuit of air conditioner for vehicles is made up of above-mentioned compressor, vaporizer, expansion valve, condenser etc.In addition, the diagram of vaporizer, expansion valve, condenser and each pipe arrangement is omitted.
In the compressor formed as described above, rotated by live axle 3, thus swash plate 5 rotates, and each piston 9 moves back and forth in each cylinder holes 21a.Therefore, pressing chamber 57 and piston stroke make volume-variation accordingly.Therefore, the refrigeration agent being sucked into swash plate room 25 by suction port 250 from vaporizer, and to be compressed from suction passage 39 via suction chamber 33 in pressing chamber 57.Then, discharged to discharge chamber 35 by the refrigeration agent that have compressed in pressing chamber 57, and discharge to condenser from exhaust port.
During this period, in this compressor, have to the effect such as swash plate 5, flange 51 the piston compression power that the angle of inclination of swash plate 5 is diminished.And, in this compressor, by changing the angle of inclination of swash plate 5, the stroke of piston 9 is increased and decreased, thus can volume controlled be carried out.
Specifically, in control mechanism 15, if the control valve 15c shown in Fig. 2 makes the flow of the refrigeration agent in low-pressure passage 15a circulation increase, then the refrigeration agent in discharge chamber 35 is difficult to via high-pressure passage 15b and throttle orifice 15d and is accumulated in pressure control chamber 31.Therefore, the pressure and the suction chamber 33 that control pressure chamber 13b are almost equal.Therefore, as shown in Figure 1, because acting on the piston compression power of swash plate 5, thus in actuator 13, control the volume reducing of pressure chamber 13b, and movable body 13a moves towards flange 51 side from swash plate 5 side on driving O direction, axle center.And in movable body 13a, the second movable cylinders portion 132 and the 3rd movable cylinders portion 133 enter in stationary cylinder portion 51a.
In addition simultaneously, in this compressor, swash plate 5 by the active force of the piston compression power and return spring 37 that act on self, thus to make each swash plate arm 5e, 5f slide at camming surface 51b away from driving the mode of axle center O.Therefore, in swash plate 5, roughly maintain the position of top dead center correspondence portion T, while make lower dead center side direction clockwise direction swing.Like this, in this compressor, swash plate 5 increases relative to the angle of inclination of the driving axle center O of live axle 3.Thus, in this compressor, the stroke of piston 9 increases, and each discharge capacity turned of live axle 3 becomes large.In addition, the angle of inclination of the swash plate 5 shown in Fig. 1 is the maximum tilt angles in this compressor.And when swash plate 5 is in maximum tilt angle, each swash plate arm 5e, 5f abut at primary importance P1 with camming surface 51b.
On the other hand, if the control valve 15c shown in Fig. 2 makes the flow of the refrigeration agent in low-pressure passage 15a circulation reduce, then the refrigeration agent in discharge chamber 35 is easily accumulated in pressure control chamber 31 via high-pressure passage 15b and throttle orifice 15d.Therefore, the pressure and the discharge chamber 35 that control pressure chamber 13b are almost equal, and the pressure ratio swash plate room 25 controlling pressure chamber 13b is high.Therefore, as shown in Figure 6, in actuator 13, the volume controlling pressure chamber 13b increases, and movable body 13a limit is away from flange 51, while move up towards swash plate 5 side in driving axle center O side.
Thus, in this compressor, the acting surface 134a of service portion 134 plays a role in the mode pressed towards the rear of swash plate room 25 by protuberance 5g at working position F.Therefore, each swash plate arm 5e, 5f to slide at camming surface 51b close to the mode of driving axle center O, and in swash plate 5, roughly maintain the position of top dead center correspondence portion T, while make lower dead center side direction counterclockwise swing.Like this, in this compressor, swash plate 5 reduces relative to the angle of inclination of the driving axle center O of live axle 3.Thus, in this compressor, the stroke of piston 9 reduces, and each discharge capacity turned of live axle 3 diminishes.In addition, because angle of inclination is reduced, thus swash plate 5 abuts with return spring 37.In addition, the angle of inclination of the swash plate 5 shown in Fig. 6 is minimum cant of this compressor.And when swash plate 5 is in minimum cant, each swash plate arm 5e, 5f abut at second place P2 with camming surface 51b.
Like this, in this compressor, adopt actuator 13, changed the angle of inclination of swash plate 5 by the pressure change in the control pressure chamber 13b that volume ratio swash plate room 25 is little.Therefore, in this compressor, with changed to carry out the compressor of the change at angle of inclination by the pressure in swash plate room 25 compared with, the amount of the refrigeration agent needed for change at angle of inclination can be reduced.Therefore, in this compressor, the maximization of swash plate room 25 and then housing 1 can be suppressed.
In addition, in this compressor, the rotation of flange 51 is passed to swash plate 5 by each swash plate arm 5e, 5f of linkage mechanism 7, and not only roughly maintains the position of the top dead center correspondence portion T of swash plate 5 but also allow the change at angle of inclination.In addition, the service portion 134 of movable body 13a and the protuberance 5g of swash plate 5 are respectively from the top dead center corresponding portion T lateral deviation heart driving axle center O to swash plate 5.When the acting surface 134a of above-mentioned service portion 134 and protuberance 5g reduces the angle of inclination of swash plate 5 at working position F point cantact, acting surface 134a presses protuberance 5g.And this working position F moves along with the change at angle of inclination.
Specifically, as shown in (A) of Fig. 7, in this compressor, when angle of inclination is maximum, working position F is positioned at the T side, top dead center correspondence portion of swash plate 5.Then, angle of inclination diminishes, and each swash plate arm 5e, 5f and camming surface 51b moves to second place P2 side.Therefore, in this compressor, as shown in the white arrow of (B) of Fig. 7, if the angle of inclination of swash plate 5 diminishes, then working position F moves towards axis of rotation O side.In other words, compared with working position F when working position F when angle of inclination is maximum and angle of inclination are minimum, closer to the top dead center correspondence portion T of swash plate 5.Here, in this compressor, even if when angle of inclination is minimum, working position F also can not cross and move to the side that T side, portion corresponding to top dead center is contrary with driving axle center O.
Therefore, in this compressor, when reducing angle of inclination, with working position F compared with the situation of the constant distance of driving axle center O, even without the variable differential pressure of increase to guarantee larger thrust, movable body 13a also can be made to move.That is, in this compressor, the load of movable body 13a when angle of inclination is diminished can be reduced.Therefore, in this compressor, the variable quantity of variable differential pressure during change angle of inclination diminishes, and easily promptly changes angle of inclination according to the operational situation of carried vehicle, thus can play higher controlling.
In addition, in this compressor, because working position F moves because of the change at the angle of inclination of swash plate 5 as described above, so when range of tilt angles is identical, with working position F compared with the compressor of the constant distance of driving axle center O, the stroke in the O direction, driving axle center of movable body 13a diminishes.Thus, in this compressor, the maximization of axial length can be suppressed.For above-mentioned each effect, by being more specifically described with the contrast of comparative example.
The compressing mechanism of comparative example becomes, and part changes swash plate 5 and the movable body 13a of the compressor of embodiment 1, and does not arrange protuberance 5g and service portion 134.Thus, in the compressor of comparative example, the rear end in the first movable cylinders portion 131 of movable body 13a abuts with front surface 5a around inserting hole 5d.Therefore, in the compressor of comparative example, movable body 13a and swash plate 5 drive the position on the O of axle center to abut being roughly in.Thus, in this compressor, when changing the angle of inclination of swash plate 5, the working position of movable body 13a and swash plate 5 changes abreast with driving O direction, axle center.That is, in the compressor of comparative example, even if when angle of inclination creates change, the distance of working position and driving axle center O is also constant and do not change.
Therefore, in the compressor of comparative example, as shown in the coordinate diagram of Fig. 8, when reducing angle of inclination, need increase variable differential pressure and utilize larger thrust that movable body 13a is moved.On the other hand, in the compressor of embodiment 1, as described above, even without the variable differential pressure of increase to guarantee larger thrust, movable body 13a also can be made to move.Therefore, in the compressor of embodiment 1, when can make change angle of inclination, required variable differential pressure diminishes and roughly even on the whole.
In addition, as shown in Figure 9, in the compressor of comparative example, be the swash plate 5 (with reference to double dot dash line) under maximum state for this figure medium dip angle, when to be indexed to angle of inclination making it be minimum state, movable body 13a needs along driving O direction, axle center displacement distance S2.
On the other hand, in the compressor of embodiment 1, be the swash plate 5 under maximum state for angle of inclination, when making angle of inclination be indexed to minimum state, as long as movable body 13a is along driving O direction, axle center displacement distance S1, it is enough.That is, the compressor of embodiment 1 is compared with the compressor of comparative example, and the stroke in the O direction, driving axle center of movable body 13a diminishes.
Therefore, the compressor of embodiment 1 can either play higher controlling and can play excellent lift-launch again.
Particularly in this compressor, directly to abut with swash plate 5 via service portion 134 and protuberance 5g due to movable body 13a and it pressed, thus act on the load of swash plate 5 towards being difficult to change.Therefore, in this compressor, swash plate 5 easily presses towards driving O direction, axle center by movable body 13a, thus movable body 13a stably can change the angle of inclination of swash plate 5.In addition, in this compressor, due to the stable posture of movable body 13a, so be also difficult to produce the pressure leakage controlled in pressure chamber 13b.
In addition, in this compressor, when the change at angle of inclination carrying out swash plate 5, only make movable body 13a directly abut with swash plate 5 and press it, do not utilize connection pin etc. to be linked with protuberance 5g by service portion 134.Therefore, in this compressor, there is not the worry posture of movable body 13a being changed because of the structure of linking portion, and when carrying out the change at angle of inclination, the posture of movable body 13a is difficult to change.In addition, in this compressor, the complicated of structure can be suppressed, thus cheapization of manufacture cost can be realized.
Further, in this compressor, because movable body 13a inserts for live axle 3, and movable body 13a is received at stationary cylinder portion 51a, thus can be chimeric with flange 51 by movable body 13a.Here, in this compressor, the 3rd movable cylinders portion 133 of movable body 13a enters to the position of the inner side of thrust-bearing 55 in stationary cylinder portion 51a.Therefore, in this compressor, can either axial length be shortened, between flange 51 and swash plate 5, suitably can guarantee again the space for driving axle center O direction movement for movable body 13a edge.In addition, in this compressor, owing to being provided with thrust-bearing 55, thus can suitably supporting role in suction reaction force, the compression reaction force of piston 9.
In addition, in this compressor, utilize stationary cylinder portion 51a thus can between flange 51 and movable body 13a suitably formation control pressure chamber 13b.And, in this compressor, utilize O type ring 49c, 49d of being arranged at the first, the 3rd movable cylinders portion 131,133 respectively, thus suitably guarantee the tightness controlling pressure chamber 13b.
Further, in this compressor, service portion 134 and protuberance 5g from driving axle center O to the top dead center correspondence portion T lateral deviation heart, and if swash plate 5 angle of inclination diminish, then working position F is as described above to driving O side, axle center to move.Therefore, in this compressor, the change at angle of inclination can not be hindered, between flange 51 and swash plate 5, easily guarantee the space for driving axle center O direction movement for movable body 13a edge.Therefore, in this compressor, the large footpath of actuator 13 can be made, thus can utilize enough thrust that movable body 13a is promptly moved.In this, in this compressor, also promptly can change angle of inclination according to the operational situation of vehicle.
In addition, in this compressor, service portion 134 is arranged at the T side, top dead center correspondence portion of swash plate 5 highlightedly in the first movable cylinders portion 131, and forms as one with movable body 13a.In addition, acting surface 134a is formed with at service portion 134.Therefore, in this compressor, from driving axle center O on the position of the top dead center correspondence portion T lateral deviation heart, acting surface 134a can be made easily to abut with protuberance 5g.Here, because protuberance 5g is formed as hemispherical giving prominence to, so can make acting surface 134a and protuberance 5g suitably point cantact in approximate.Therefore, in this compressor, the area of contact of acting surface 134a and protuberance 5g can be reduced, thus make swash plate 5 easily change angle of inclination.
Further, protuberance 5g is integrally formed in the front surface 5a of swash plate main body 50.Therefore, in this compressor, can the minimizing of achievement unit pieces number, thus easily carry out manufacturing and the minimizing of manufacture cost can be realized.
In addition, in this compressor, swash plate room 25 is communicated with by suction passage 39 with suction chamber 33.Thus, in this compressor, can make swash plate room 25 in the same manner as suction chamber 33 is low pressure.
Further, control mechanism 15 is adjusted by the aperture of control valve 15c, thus the pressure in adjustment pressure control chamber 31 and then in control pressure chamber 13b.And axle road 3a and pathway 3b is formed in live axle 3.Thus, in this compressor, control mechanism 15 miniaturization can be made and can pressure suitably in Variation control pressure chamber 13b, thus movable body 13a can be made suitably to move.
In addition, in this compressor, utilize O type ring 49a, 49b of being arranged at the rear end of live axle 3, thus suitably guarantee the tightness of pressure control chamber 31.
(embodiment 2)
As shown in Figure 10, in the compressor of embodiment 2, swash plate 5 has swash plate main body 50, swash plate arm 5e, 5f and contact component 59.This contact component 59 is also equivalent to of the present inventionly be applied portion.
To be split with swash plate main body 50, mode is formed contact component 59.Contact component 59 is installed on each between swash plate arm 5e, 5f at the front surface 5a of swash plate main body 50, and is positioned at the position from driving axle center O to the top dead center correspondence portion T lateral deviation heart of swash plate 5.
Protuberance 59a outstanding is toward the front formed at this contact component 59.This protuberance 59a is formed as approximate hemispherical.Protuberance 59a is at the acting surface 134a point cantact of working position F and service portion 134.Like this, in this compressor, by acting surface 134a and protuberance 59a, service portion 134 is abutting from the position driving axle center O to the top dead center corresponding portion T lateral deviation heart of swash plate 5 with contact component 59.Other structures of this compressor are identical with the compressor of embodiment 1, mark identical reference character and omit the detailed description relevant to structure for identical structure.
In this compressor, because swash plate 5 and contact component 59 are split, so the degrees of freedom of design of swash plate main body 50, contact component 59 can be improved.Other effects of this compressor are identical with the compressor of embodiment 1.
Above, describe the present invention according to embodiment 1,2, but the present invention is not limited to above-described embodiment 1,2, certainly can carries out suitable change to be applied in the scope not departing from its purport.
Such as, in the compressor of embodiment 1,2, also can be configured to during the angle of inclination of swash plate 5 is decreased to predetermined angular from maximum state, working position F moves towards driving O side, axle center, during becoming minimum cant from predetermined angular, working position F does not move.
In addition, also protuberance 5g, protuberance 59a can be formed as plane, and the acting surface 134a of service portion 134 is formed as curved.Thereby, it is possible to make protuberance 5g, contact component 59 at working position F and service portion 134 linear contact lay.
Further, for control mechanism 15, also can be configured to arrange control valve 15c at high-pressure passage 15b, and throttle orifice 15d is set at low-pressure passage 15a.In this case, utilize control valve 15c, the flow of the refrigeration agent of the high pressure in high-pressure passage 15b circulation can be adjusted.Thereby, it is possible to make control pressure chamber 13b become high pressure rapidly by the high pressure in discharge chamber 35, and the rapid minimizing of compression volume can be carried out.In addition, also can replace control valve 15c ground, the three-way valve be connected with low-pressure passage 15a and high-pressure passage 15b is set, and by adjusting the aperture of three-way valve, thus adjust the flow of the refrigeration agent circulated in low-pressure passage 15a, in high-pressure passage 15b.
Industrial utilizes possibility
The present invention can be applied to aircondition etc.
The explanation of reference character
1 ... housing; 3 ... live axle; 3a ... axle road (control access); 3b ... pathway (control access); 5 ... swash plate; 5d ... inserting hole; 5e, 5f ... swash plate arm (transferring elements); 5g ... protuberance (being applied portion); 7 ... linkage mechanism; 9 ... piston; 11a, 11b ... crawler shoe (switching mechanism); 13 ... actuator; 13a ... movable body; 13b ... control pressure chamber (control access); 15 ... control mechanism; 15a ... low-pressure passage (control access); 15b ... high-pressure passage (control access); 15c ... control valve; 25 ... swash plate room; 31 ... pressure control chamber; 33 ... suction chamber; 35 ... discharge chamber; 21a ... cylinder holes; 49a, 49b ... O type ring (the 3rd sealing component); 49c ... O type ring (the first sealing component); 49d ... O type ring (the second sealing component); 51 ... flange (protruding part); 51a ... stationary cylinder portion; 55 ... thrust-bearing; 59 ... contact component (being applied portion); 59a ... protuberance; 131 ... first movable cylinders portion (movable cylinders portion); 132 ... second movable cylinders portion (movable cylinders portion); 133 ... 3rd movable cylinders portion (movable cylinders portion); 134 ... service portion; F ... working position; O ... drive axle center; T ... top dead center correspondence portion.

Claims (14)

1. a capacity variable type tilted-plate compressor, is characterized in that, possesses:
Housing, it is formed with swash plate room and cylinder holes;
Live axle, it can be supported on described housing rotatably;
Swash plate, it can by the rotation of described live axle in the indoor rotation of described swash plate;
Linkage mechanism, it is arranged between described live axle and described swash plate, and the change at the angle of inclination in the direction allowing described swash plate orthogonal relative to the driving axle center with described live axle;
Piston, it can reciprocatingly be accommodated in described cylinder holes;
Switching mechanism, its rotation by described swash plate and described piston is moved back and forth in described cylinder holes with the stroke corresponding with described angle of inclination;
Actuator, it can change described angle of inclination; And
Control mechanism, it controls described actuator,
Described linkage mechanism has: protruding part, and it is fixed on described live axle in described swash plate indoor; And transferring elements, the rotation of described protruding part is passed to described swash plate by it;
Described actuator has: described protruding part; Movable body, it can rotate integrally with described swash plate, and can move along described driving axis direction thus change described angle of inclination; And control pressure chamber, it is divided by described protruding part and described movable body, and by changing inner pressure by described control mechanism thus making described movable body move,
Being formed at described movable body can by the pressure in described control pressure chamber to press the service portion of described swash plate,
Be formed at described swash plate and abut with described service portion and the portion that is applied be pressed,
Described service portion abuts at working position with the described portion that is applied,
Described working position is moved by the change at described angle of inclination,
The top dead center correspondence portion making described piston be positioned at top dead center is had in described swash plate definition,
Compared with described working position when being minimum with described angle of inclination, described working position when described angle of inclination is maximum is closer to described top dead center correspondence portion.
2. capacity variable type tilted-plate compressor according to claim 1, is characterized in that,
Described live axle is through described movable body, and described movable body can be chimeric with described protruding part.
3. capacity variable type tilted-plate compressor according to claim 2, is characterized in that,
Described movable body has the movable cylinders portion of the cylindrical shape being formed as coaxial with described driving axle center,
Described protruding part has cylindric stationary cylinder portion, and the stationary cylinder portion of this cylindrical shape is formed as the cylindrical shape coaxial with described driving axle center at the outer circumferential side in described movable cylinders portion, and guarantees described control pressure chamber in described movable cylinders portion.
4. capacity variable type tilted-plate compressor according to claim 3, is characterized in that,
The first sealing component that described control pressure chamber is sealed is provided with between described movable cylinders portion and described live axle,
The second sealing component that described control pressure chamber is sealed is provided with between described movable cylinders portion and described stationary cylinder portion.
5. the capacity variable type tilted-plate compressor according to claim 3 or 4, is characterized in that,
The thrust-bearing bearing the thrust acting on described piston is provided with between described housing and described protruding part,
It is less than described thrust-bearing and can be fitted in described thrust-bearing that described movable cylinders portion is formed as diameter.
6. the capacity variable type tilted-plate compressor according to any one of Claims 1 to 5, is characterized in that,
Described service portion and be describedly applied portion mutual point cantact or linear contact lay on described working position.
7. capacity variable type tilted-plate compressor according to claim 6, is characterized in that,
Described service portion and described in be applied portion from described driving axle center to the described top dead center correspondence portion lateral deviation heart,
If described angle of inclination diminishes, then described working position moves to side, described driving axle center.
8. capacity variable type tilted-plate compressor according to claim 7, is characterized in that,
Described service portion has the acting surface extended along the direction orthogonal with described driving axle center,
The described portion of being applied has gives prominence to and the protuberance abutted with described acting surface from described swash plate.
9. the capacity variable type tilted-plate compressor according to claim 7 or 8, is characterized in that,
Described movable body has the movable cylinders portion of the cylindrical shape being formed as coaxial with described driving axle center,
Described service portion is arranged at the side, described top dead center correspondence portion in described movable cylinders portion highlightedly.
10. the capacity variable type tilted-plate compressor according to any one of claim 1 ~ 9, is characterized in that,
Described swash plate has: swash plate main body, and it is formed with the inserting hole passed for described live axle; And described in be applied portion, it is integrally formed in described swash plate main body.
11. capacity variable type tilted-plate compressors according to any one of claim 1 ~ 9, is characterized in that,
Described swash plate has: swash plate main body, and it is formed with the inserting hole passed for described live axle; And described in be applied portion, it is fixed on described swash plate main body.
12. capacity variable type tilted-plate compressors according to any one of claim 1 ~ 11, is characterized in that,
Suction chamber and discharge chamber is formed at described housing,
Described suction chamber is communicated with described swash plate room.
13. capacity variable type tilted-plate compressors according to claim 12, is characterized in that,
Described control mechanism has: control access, and described control pressure chamber is communicated with described suction chamber and/or described discharge chamber by it; And control valve, it can adjust the aperture of described control access,
Being formed at least partially in described live axle of described control access.
14. capacity variable type tilted-plate compressors according to claim 13, is characterized in that,
Between described housing and one end of described live axle, be formed with pressure control chamber, this pressure control chamber is communicated with described control pressure chamber via described control access and is changed pressure by described control valve,
The 3rd sealing component that described pressure control chamber is sealed is provided with between described housing and described live axle.
CN201480050320.6A 2013-09-11 2014-09-10 Variable-capacity swash plate compressor Active CN105556121B (en)

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6146263B2 (en) * 2013-11-06 2017-06-14 株式会社豊田自動織機 Variable capacity swash plate compressor
AU2018295108B2 (en) * 2017-06-27 2022-06-30 CW Holdings, Ltd. Variable stroke pump
US11047373B2 (en) * 2018-03-30 2021-06-29 Kabushiki Kaisha Toyota Jidoshokki Piston compressor including a suction throttle

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5486098A (en) * 1992-12-28 1996-01-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
CN101120169A (en) * 2004-12-14 2008-02-06 (学)斗源学院 Variable displacement swash plate type compressor with smooth inclined moving feature
CN101512151A (en) * 2006-09-08 2009-08-19 康奈可关精株式会社 Variable displacement compressor
CN103216411A (en) * 2012-01-19 2013-07-24 株式会社丰田自动织机 Swash plate type variable displacement compressor and method of controlling solenoid thereof
KR20130092878A (en) * 2012-02-13 2013-08-21 한라비스테온공조 주식회사 Swash plate type variable capacity compressor

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2618222A (en) * 1947-05-12 1952-11-18 Rolls Royce Fuel system for gas-turbine engines
US4037993A (en) * 1976-04-23 1977-07-26 Borg-Warner Corporation Control system for variable displacement compressor
US4061443A (en) 1976-12-02 1977-12-06 General Motors Corporation Variable stroke compressor
US4108577A (en) * 1977-06-09 1978-08-22 General Motors Corporation Variable displacement compressor
JPS61145379A (en) * 1984-12-17 1986-07-03 Nippon Denso Co Ltd Variable displacement compressor
JPH0518355A (en) * 1991-07-15 1993-01-26 Toyota Autom Loom Works Ltd Variable capacity type compressor
JPH05172052A (en) * 1991-12-18 1993-07-09 Sanden Corp Variable displacement swash plate type compressor
JPH05312144A (en) * 1992-05-08 1993-11-22 Sanden Corp Variable displacement swash plate type compressor
JPH07279840A (en) * 1994-04-11 1995-10-27 Sanden Corp Swash type variable displacement compressor
JPH07310653A (en) * 1994-05-12 1995-11-28 Sanden Corp Swash plate type variable displacement compressor
JPH0814159A (en) * 1994-06-27 1996-01-16 Sanden Corp Cam plate type variable capacity compressor
DE19939131A1 (en) * 1999-08-18 2001-03-08 Zexel Gmbh Axial piston engine with an infinitely adjustable piston stroke
US6354809B1 (en) * 2000-01-27 2002-03-12 Ford Global Technologies, Inc. Variable swash plate compressor
JP2002130120A (en) * 2000-10-24 2002-05-09 Toyota Industries Corp Displacement controller for variable displacement compressor
JP4399994B2 (en) * 2000-11-17 2010-01-20 株式会社豊田自動織機 Variable capacity compressor
JP4976731B2 (en) * 2006-04-07 2012-07-18 カルソニックカンセイ株式会社 Variable capacity compressor
JP2009133252A (en) * 2007-11-30 2009-06-18 Toyota Industries Corp Variable displacement type one side swash plate compressor
JP2009209910A (en) * 2008-03-06 2009-09-17 Toyota Industries Corp Swash plate compressor
JP5519193B2 (en) * 2009-06-05 2014-06-11 サンデン株式会社 Variable capacity compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5486098A (en) * 1992-12-28 1996-01-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
CN101120169A (en) * 2004-12-14 2008-02-06 (学)斗源学院 Variable displacement swash plate type compressor with smooth inclined moving feature
CN101512151A (en) * 2006-09-08 2009-08-19 康奈可关精株式会社 Variable displacement compressor
CN103216411A (en) * 2012-01-19 2013-07-24 株式会社丰田自动织机 Swash plate type variable displacement compressor and method of controlling solenoid thereof
KR20130092878A (en) * 2012-02-13 2013-08-21 한라비스테온공조 주식회사 Swash plate type variable capacity compressor

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DE112014004173T5 (en) 2016-05-25
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JPWO2015037636A1 (en) 2017-03-02
WO2015037637A1 (en) 2015-03-19
KR20160052682A (en) 2016-05-12
US20160222952A1 (en) 2016-08-04
WO2015037636A1 (en) 2015-03-19
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DE112014004156B4 (en) 2019-11-21
US20160222953A1 (en) 2016-08-04

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