CN1828052A - Swash plate type variable displacement compressor - Google Patents

Swash plate type variable displacement compressor Download PDF

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Publication number
CN1828052A
CN1828052A CNA2006100587815A CN200610058781A CN1828052A CN 1828052 A CN1828052 A CN 1828052A CN A2006100587815 A CNA2006100587815 A CN A2006100587815A CN 200610058781 A CN200610058781 A CN 200610058781A CN 1828052 A CN1828052 A CN 1828052A
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CN
China
Prior art keywords
swash plate
wedge
live axle
displacement
imaginary plane
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CNA2006100587815A
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Chinese (zh)
Inventor
太田雅树
中山治
金井明信
山之内亮人
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
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 CN1828052A publication Critical patent/CN1828052A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • F04B27/1018—Cylindrical 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
    • F04B27/1081—Casings, housings
    • 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
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping 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
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Abstract

A swash plate type variable displacement compressor includes a housing, a drive shaft, a piston, a lug plate, a swash plate, a hinge mechanism provided between the lug plate and the swash plate, and a control mechanism. The hinge mechanism includes a restraining hinge element that is located on a suction side with respect to a first imaginary plane that includes a top position of the swash plate corresponding to the top dead center position of the piston and the axis of the drive shaft for restraining the lug plate and the swash plate from rotating relative to each other and the swash plate to move away from the lug plate. The hinge mechanism further includes a non-restraining hinge element that is located on a discharge side with respect to the first imaginary plane for not restraining the swash plate from moving away from the lug plate.

Description

Displacement-variable swashplate compressor
Technical field
The present invention relates to a kind of displacement-variable swashplate compressor.
Background technique
Japanese Patent Application No.9-203377 has disclosed a kind of displacement-variable swashplate compressor (abbreviating " compressor " when hereinafter relating to as) of routine.This compressor comprises: shell limits cylinder thorax, arbor chamber, suction chamber and discharge side therein; Piston, it is contained in the cylinder thorax in the to-and-fro motion mode, is used to limit compression chamber; And, live axle, it is driven by external drive source, and is supported by the shell rotary way.This compressor further comprises: wedge, and it is supported in the arbor chamber, to turn round jointly with live axle; And swash plate, be supported in the shell (arbor chamber), with by wedge and movable joint mechanism, swash plate is tilted with the common revolution of live axle and with respect to live axle, be used for making reciprocating motion of the pistons by piston shoes.Swash plate is formed centrally the through hole with parallel apparent surface therein, is used to hold the outer circumferential face of live axle, and live axle is through in the through hole.In addition, compressor comprises control mechanism, is used for the pressure of controller axocoel.
The movable joint mechanism of compressor comprises arm spare and engaging groove, as unrestricted movable section part, it orientates as adjacent corresponding to the tip position of piston top dead center position with swash plate, and be positioned on the imaginary plane that comprises this tip position and drive axis, unrestricted movable section part does not limit swash plate and removes from wedge.Arm spare is arranged on the swash plate, and has first guide surface towards wedge.Engaging groove then is formed in the wedge, and has second guide surface, and second guide surface can contact with first guide surface.In unrestricted movable section part, arm spare top is remained in the engaging groove, thereby restriction wedge and swash plate relatively rotate with respect to each other.
Gou Zao compressor as mentioned above is configured for the refrigerating circuit of vehicle jointly with condenser, expansion valve and vaporizer.When by live axle being driven, and when swash plate is rotated with the inclination angle, make piston to-and-fro motion in the cylinder thorax as motor of external drive source etc.Therefore, refrigerant gas is extracted out and made it enter compression chamber the cylinder thorax from suction chamber, refrigerant gas is compressed, then refrigerant gas is discharged and make it enter discharge side.Control mechanism is regulated the pressure in the arbor chamber, with the inclination angle of change swash plate, thus the amount that control enters the refrigerant gas of discharge side from the compression chamber discharge.Therefore, by refrigerating circuit, obtain the cooling effect of corresponding refrigerant gas discharge capacity.
During compressor operation,, the compression reaction force and the inhalation power of refrigerant gas put on swash plate by piston and piston shoes, thereby set up moment thereon, this moment promotes swash plate, make swash plate around its with above-mentioned imaginary plane between the intersection revolution so that the inclination of swash plate relative drive shaft.In unrestricted movable section part, arm spare top is remained in the engaging groove, two sides of arm spare are contacted with the interior sidewall surface of engaging groove respectively, thereby bear this moment.The through hole that is formed at the swash plate center bears this moment at its parallel apparent surface place.
Japanese patent gazette No.2917767 has disclosed a kind of compressor, and the movable joint mechanism that it has is different with above-mentioned movable joint mechanism.In this compressor, movable joint mechanism comprises a pair of restriction movable section part, its above-mentioned relatively imaginary plane lays respectively at the suction side and discharges side, replace above-mentioned arm spare and engaging groove as unrestricted movable section part, be used to limit wedge and swash plate relatively rotates with respect to each other, and the restriction swash plate is removed from wedge.Each limits movable section part and comprises: support arm, and it is arranged on the wedge and has bullport; And, guide finge, it is arranged on the swash plate, and has spherical portion, is used for sliding at bullport.
In the compressor of above-mentioned Japanese patent gazette No.2917767, identical with the compressor among the Japanese patent gazette No.9-203377, by the inclination angle of the pressure in the control mechanism adjusting arbor chamber with the change swash plate, thereby control enters the refrigerant gas amount of discharge side from compression chamber.
During compressor operation, paired restriction movable section part bears the moment that promotes swash plate, this moment make swash plate around its with above-mentioned imaginary plane between the intersection revolution, thereby make the inclination of swash plate relative drive shaft.Similarly, the through hole that is formed on the swash plate center also bears this moment at its parallel apparent surface place.
Yet, in the above-mentioned compressor, have problem hereinafter described aspect vibration during reducing compressor operation and the noise.
In the compressor of Japanese patent gazette No.9-203377, when compressor turns round under high speed and big discharge capacity, under the state of the lack of refrigerant in refrigerating circuit, piston is with to-and-fro motion in bigger length of stroke at a high speed, but because the refrigerant gas deficiency does not increase to expected value with head pressure.Therefore, the inertial force of piston is tending towards becoming greater than compression reaction force, promotes the moment that swash plate increases its inclination angle on the swash plate thereby set up to act on.The movable joint mechanism of Japanese patent gazette No.9-203377 has unrestricted movable section part, and it is the function removed from wedge of swash plate without limits, does not bear by the excessive inertial force of piston and causes, and promote the above-mentioned moment that swash plate further tilts.Therefore, exist swash plate to tilt to surpass worrying of its inclination maximum.In this case, piston to-and-fro motion in greater than the distance of maximum stroke, and piston head is at the roof place of compression chamber bump suction valve, and the result who brings produces extraordinary noise and vibration.
In the compressor of Japanese patent gazette No.2917767, because movable joint mechanism has paired restriction movable section part, its restriction swash plate is removed from wedge, so the above-mentioned excessive inertial force that movable joint mechanism bears by piston causes and promote the moment that swash plate further tilts.Therefore, swash plate can not exceed its inclination maximum and tilt, thereby the excessive inclination of avoiding exceeding the inclination maximum degree owing to swash plate produces extraordinary noise and vibration.
Yet in the compressor of Japanese patent gazette No.2917767, each limits movable section part restriction wedge and swash plate relatively rotates with respect to each other, and the restriction swash plate is removed from wedge, and, to move in order to guarantee the level and smooth of movable joint mechanism, each gap of limiting movable section part needs suitably to enlarge.This is because normally mass production of compressor is considered to be difficult to the cost of production and the productivity of compressor when reducing to limit the gap of movable section part, guarantees the Location accuracy of restriction movable section part.The big gap of restriction movable section part may cause between swash plate and the piston shoes, also have the shifting amount (gap) between piston shoes and the piston.When compressor turned round under its minimum injection rate, the compression reaction force and the inhalation power that act on the swash plate became minimum, so, in compressor, may produce unusual and undesirable noise and vibration around swash plate, piston shoes and piston.This compressor is installed in the vehicle, may make the occupant in the vehicle feel uncomfortable.
The present invention is devoted to a kind of reduce noise and the displacement-variable swashplate compressor that vibrates generation in the running.
Summary of the invention
According to the present invention, a kind of displacement-variable swashplate compressor that is used for the compressed refrigerant agent comprises shell, live axle, piston, wedge, swash plate, movable joint mechanism and control mechanism.In shell, limit cylinder thorax, arbor chamber, suction chamber and discharge side.Piston is contained in the cylinder thorax in the to-and-fro motion mode, and limits compression chamber in the cylinder thorax.Live axle is driven by external drive source, and is supported with rotary way by shell.Wedge is supported by live axle in the arbor chamber, so that it is with drive shaft turns.Swash plate is supported by live axle in the arbor chamber.Movable joint mechanism is arranged between wedge and the swash plate.By wedge and movable joint mechanism, but swash plate can be tilted with drive shaft turns and relative drive shaft, be used for making reciprocating motion of the pistons by piston shoes.Control mechanism is steerable, with the pressure in the controller axocoel, thereby by the to-and-fro motion of piston based on swashplate angle, changes the amount that enters the freezing mixture the discharge side from the compression chamber discharge.Movable joint mechanism comprises the restriction movable section part, its relative first imaginary plane is positioned at the suction side, first imaginary plane comprises the axis of swash plate and corresponding tip position of piston top dead center position and live axle, the restriction movable section part is used to limit wedge and swash plate relatively rotates with respect to each other, and the restriction swash plate is removed from wedge.Movable joint mechanism further comprises unrestricted movable section part, and its relative first imaginary plane is positioned at the discharge side, and unrestricted movable section part does not limit swash plate and removes from wedge.
Description of drawings
In claims, propose to think feature of the present invention especially with novelty.With reference to the detailed description of hereinafter in conjunction with the accompanying drawings preferred implementation being carried out, will understand the present invention better together with its purpose and advantage, wherein:
Fig. 1 is the longitudinal sectional view of displacement-variable swashplate compressor according to the preferred embodiment of the present invention;
Fig. 2 is when watch the sectional view of the part amplification of compressor according to the preferred embodiment of the present invention from Fig. 1 inboard;
Fig. 3 is the top view of swash plate according to the preferred embodiment of the present invention;
Fig. 4 is the front elevation of swash plate according to the preferred embodiment of the present invention;
Fig. 5 is the sectional view that amplify the part of compressor according to the preferred embodiment of the present invention, and the diagram swash plate is in the inclination at minimum angle-of-incidence place;
Fig. 6 ought watch the sectional view of the part amplification of compressor according to the preferred embodiment of the present invention from Fig. 1 inboard, and the diagram swash plate is in the inclination at minimum angle-of-incidence place; And
Fig. 7 is the schematic top view of swash plate, movable joint mechanism and wedge according to the preferred embodiment of the present invention, the relation between diagram wedge and the swash plate.
Embodiment
Referring to figs. 1 through Fig. 7, hereinafter describe according to preferred implementation of the present invention.With reference to Fig. 1, the displacement-variable swashplate compressor 10 of preferred implementation (hereafter is " compressor ") has shell 1, single head pison 31, live axle 16, wedge 24, swash plate 25 and control mechanism 4.In Fig. 1, the left side is corresponding with the front side and the rear side of compressor 10 respectively with the right side.
Shell 1 comprises: cylinder body 11; Fore shell 12 combines with the front end of cylinder body 11; And back cover 13, combine by the rear end of valve plate 14 with cylinder body 11.Fore shell 12 and back cover 13 are fixed in cylinder body 11 by the bolt (not shown).Cylinder body 11 and fore shell 12 limit arbor chamber 15 jointly therein.
Live axle 16 is supported by cylinder body 11 and fore shell 12 rotary way.More specifically, be formed centrally axis hole 80 in cylinder body 11, helical spring 17 and thrust bearing 18 are arranged in the axis hole 80, live axle 16 is supported by thrust bearing 18 in its back-end, and pushes away this thrust bearing 18 before the helical spring 17.In addition, in the position that live axle 16 approaches its front end, by radial bearing 19 supporting driving shafts 16, radial bearing 19 is arranged in the axis hole 81, and axis hole 81 is formed in the fore shell 12.Seal arrangement 20 is arranged on the front of radial bearing 19 in the axis hole 81.In addition, live axle 16 is connected with belt pulley 21 by bearing 90 at its front end place, belt pulley 21 is arranged on the front end of fore shell 12.Belt pulley 21 can rotate with live axle 16.By belt 91, belt pulley 21 is connected with vehicle motor as external drive source.Therefore, during engine running, continue compressor 10 is driven by motor.
Wedge 24 is pressed on the live axle 16 that fits in the arbor chamber 15.Thrust bearing 27 is arranged between the internal face of wedge 24 and fore shell 12.Swash plate 25 is installed on the live axle 16 and has through hole 22, and live axle 16 is through in the through hole 22.Through hole 22 is formed on the center of swash plate 25, and has parallel apparent surface 23, is used to hold the outer circumferential face of live axle 16, as shown in Figure 3 and Figure 4.Movable joint mechanism 26 is arranged between wedge 24 and the swash plate 25.
With reference to Fig. 1, between wedge 24 and swash plate 25, spring 28 is arranged on the live axle 16.Spring 28 is used for pushing swash plate 25 to cylinder body 11, that is the direction that reduces at the inclination angle that causes swash plate 25.In the back of swash plate 25, circlip 29 is fixed on the live axle 16.Spring 30 is arranged on the live axle 16 between the circlip 29 and swash plate 25.When being subjected to swash plate 25 extruding, spring 30 is used to promote swash plate 25 away from cylinder body 11, that is, the direction that increases at the inclination angle that causes swash plate 25.
Cylinder body 11 defines a plurality of cylinder thorax 11a therein, and its equal angles mode is arranged in around the live axle 16.Only show a cylinder thorax 11a among the figure.Each cylinder thorax 11a is parallel to live axle 16 and extends, and, but piston 31 is arranged among the cylinder thorax 11a in the to-and-fro motion mode.Each piston 31 engages with the periphery of swash plate 25 at piston 31 front ends by a pair of piston shoes 32.Each piston shoes 32 has: semispherical surface roughly contacts with piston 31; And the plane, contact with swash plate 25.Paired piston shoes 32 are arranged in the opposite side of swash plate 25, and it is roughly spherical to make them form.
In each cylinder thorax 11a, compression chamber 33 is defined between the piston head and valve plate 14 of the piston 31 of back.When swash plate 25 rotates with live axle 16, swash plate 25 tilts with respect to live axle 16 simultaneously, makes swash plate 25 produce oscillating motions, thereby, by the paired piston shoes 32 of association, make each piston 31 to-and-fro motion.By this way, by swash plate 25 and piston shoes 32, the rotation of live axle 16 is changed into the to-and-fro motion of piston 31.
Back cover 13 limits discharge side 34 therein and centers on the annular suction chamber 35 of discharge side 34.Suction chamber 35 is connected in the downstream side by import 36 and refrigerating circuit 37, and import 36 is formed in the back cover 13.Discharge side 34 is connected at upstream side with refrigerating circuit 37 by exporting 38, and outlet 38 is formed in the back cover 13.Refrigerating circuit 37 comprises condenser 39, expansion valve 40 and vaporizer 41.
For each compression chamber 33, valve plate 14 has the suction port 42 and the exhaust port 43 of corresponding layout.With respect to each suction port 42 and each exhaust port 43, valve plate 14 also has corresponding suction valve 42a and the expulsion valve 43a that arranges.During the suction stroke of piston 31, by in its related suction port 42 suction compression chambers 33, push the refrigerant gas in the suction chamber 35 open suction valve 42a simultaneously.On the other hand, during the compression stroke of piston 31, in compression chamber, refrigerant gas is compressed, by its related exhaust port 43 refrigerant gas is discharged in the discharge side 34 then, push expulsion valve 43a simultaneously open.
Inlet air pathway 44 is formed in cylinder body 11, valve plate 14 and the back cover 13, is used to connect discharge side 34 and arbor chamber 15.The path 45 of bleeding is formed in cylinder body 11, valve plate 14 and the back cover 13, is used for junctor axocoel 15 and suction chamber 35.The path 45 of bleeding has throttle orifice (orifice) (not shown) therein.As shown in Figure 1, displacement control valve 46 is arranged in the inlet air pathway 44.For instance, displacement control valve 46 structurally to Japanese Patent Application No.2003-239857 in disclose similar.Inlet air pathway 44, bleed path 45 and displacement control valve 46 formation control mechanisms 4, control mechanism 4 is steerable, with the pressure in the controller axocoel 15.
According to the variation in pressure in the suction chamber 35, control mechanism 4 is by the opening and closing of displacement control valve 46 control inlet air pathways 44, thereby increases or reduce pressure in the arbor chamber 15, the discharge capacity that is used to regulate compressor 10.When the pressure when cooling load in the less and suction chamber 35 is low, increase the open degree of displacement control valve 46, thereby increase the pressure in the arbor chamber 15, and therefore the inclination angle of swash plate 25 is reduced.As a result, the stroke of each piston 31 is reduced, thereby reduce the discharge capacity of compressor 10.On the other hand, when cooling load is higher than the pressure in big and the suction chamber 35, reduce the open degree of displacement control valve 46, thereby reduce the pressure in the arbor chamber 15, the result increases the inclination angle of swash plate 25, and the stroke of each piston 31 is increased, thereby increase the discharge capacity of compressor 10.Can be according to the acceleration of the method for operation such as vehicle etc., change the open degree of displacement control valve 46 from the outside.Swash plate 25 is provided with bearing surface 25a towards the surface of wedge 24, and is as mentioned below.Bearing surface 25a contacts with wedge 24, thereby, the inclination maximum of swash plate 25 is limited.
Hereinafter describe the structure of movable joint mechanism 26 in detail.In the compressor 10 of this preferred implementation, live axle 16 arrow Z indicated direction in Fig. 1 is rotated.With reference to Fig. 4, label CP represents first imaginary plane, comprises the tip position A of swash plate 25 and the longitudinal axis O1 of live axle 16 therein.The tip position A of swash plate 25 is corresponding to the top dead center position of piston 31, and, more specifically, be with piston 31 stops placed on it.Corresponding with the section of Fig. 1 basically along the section that this imaginary plane CP is got.Label SP among Fig. 4 represents second imaginary plane, and it extends perpendicular to above-mentioned plane CP.Should be noted that in Fig. 1 swash plate 25 tilts at inclination maximum.In Fig. 3 and Fig. 4, the left side and the right side of the relative first imaginary plane CP swash plate 25, respectively with compressor 10 in side suck to take place and discharge the opposite side that takes place corresponding.In other words, in Fig. 1, observer's side with and inboard, respectively with to discharge side and suction side corresponding.In Fig. 2, observer's side with and inboard, respectively with the suction side with to discharge side corresponding.That is to say that Fig. 1 is the sectional view of compressor 10, illustrate the parts that the relative first imaginary plane CP is positioned at the suction side.Fig. 2 is the sectional view of the amplification of compressor 10, illustrates the relative first imaginary plane CP and is positioned at the parts of discharging side.
Movable joint mechanism 26 comprises support arm 61 and guide finge 62, and its relative first imaginary plane CP is positioned at the suction side, as shown in Figure 1, and as restriction movable section part 60.Movable joint mechanism 26 also comprises first guide surface 71 and second guide surface 72, and the relative first imaginary plane CP is positioned at the discharge side, as shown in Figure 2, and as unrestricted movable section part 70.As shown in Figure 3 and Figure 4, the guide finge 62 and second guide surface 72 are arranged on the front surface of swash plate 25.As depicted in figs. 1 and 2, the support arm 61 and first guide surface 71 are arranged on wedge 24 on the rear surface of swash plate 25, and respectively with respect to guide finge 62 and second guide surface, 72 corresponding layouts.
In restriction movable section part 60, support arm 61 has the bullport 61a of band inner peripheral surface, and the spherical portion 62a that is arranged on guide finge 62 tops can slide in bullport 61a.Therefore, support arm 61 and guide finge 62 as restriction movable section part 60, are used for limiting wedge 24 and swash plate 25 relatively rotates with respect to each other, and restriction swash plate 25 is removed from wedge 24.
In unrestricted movable section part 70, first guide surface 71 and second guide surface 72 and can contact toward each other each other.Should be noted that unrestricted movable section part 70 does not comprise is used to limit wedge 24 and the sidewall that swash plate 25 relatively rotates with respect to each other, and does not also comprise being used to limit the sidewall that swash plate 25 is removed from wedge 24.Therefore, first guide surface 71 and second guide surface 72, as unrestricted movable section part 70, wedge 24 relatively rotates with respect to each other with swash plate 25 and limits the function that swash plate 25 is removed from wedge 24 without limits.
According to said structure, when making unrestricted movable section part 70, can be only first guide surface 71 and second guide surface 72 be formed and have highi degree of accuracy, wherein first guide surface 71 and second guide surface 72 and restriction movable section part 60 together support swash plates 25 make swash plate 25 with the expectation angle tilt.In addition, first guide surface 71 and second guide surface 72 can reduce with respect to the Location accuracy of restriction movable section part 60.Thereby, different with restriction movable joint paired in the compressor that Japanese patent gazette No.2917767 discloses, do not need to strengthen the support arm 61 of restriction movable section part 60 and the gap between the guide finge 62.Therefore, have these support arms 61 and the guide finge 62 of expecting precision, can make the gap between support arm 61 and the guide finge 62 less by manufacturing.More specifically, the precision of axial precision by guaranteeing bullport 61a and guide finge 62 and the diameter of bullport 61a and spherical portion 62a, the gap between bullport 61a and the spherical portion 62a is accomplished less easily.As a result, swash plate 25 is adaptive with restriction movable section part 60 and unrestricted movable section part 70 with less clearance (perhaps clearance).
Therefore, the restriction movable section part 60 of movable joint mechanism 26 and unrestricted movable section part 70 are arranged between swash plate 25 and the wedge 24, and play the effect of supporting swash plate 25, make the angle tilt that swash plate 25 is requiring.For instance, when swash plate 25 is tilted in minimum angle-of-incidence, as shown in Figure 5 and Figure 6, movable joint mechanism 26 supports swash plate 25, and second guide surface 72 of the guide finge 62 of restriction movable section part 60 and unrestricted movable section part 70 slides and is positioned at definite position.
Unrestricted movable section part 70 has been save and has been used to limit the sidewall that wedge 24 and swash plate 25 relatively rotate with respect to each other, and makes unrestricted movable section part 70 can alleviate on weight.
Hereinafter describe the bearing surface 25a of swash plate 25 in detail.Referring to figs. 1 through Fig. 4, the relative second imaginary plane SP, movable joint mechanism 26 is positioned at tip position A one side.Swash plate 25 is provided with bearing surface 25a towards the surface of wedge 24, and its relative first imaginary plane CP is positioned at the suction side, and the relative second imaginary plane SP then is positioned at bottom position B one side relative with tip position A.Bottom position B is corresponding with the bottom dead center position of piston 31.By to making its level and smooth machining to what wedge 24 protruded than the zonule from swash plate 25 among the 25b of counterweight portion of swash plate 25, form bearing surface 25a.In bearing surface 25a and scope that wedge 24 can contact, make the residing position of bearing surface 25a farthest from the axes O 1 of live axle 16, that is to say, from the intersection point of straight line O2 and straight line O3 farthest, its cathetus O2 passes the axis of restriction movable section part 60 and swash plate 25, straight line O3 passes the center of bearing surface 25a and perpendicular to straight line O2, as shown in Figure 4.By this way, when making swash plate 25 tilt to its inclination maximum position, as shown in Figure 1,, make bearing surface 25a be suitable for limiting swash plate 25 and exceed inclination maximum by contacting with wedge 24.
The compressor 10 of the above preferred implementation is formed the refrigerating circuit of using in the vehicle for example 37 with condenser 39, expansion valve 40 and vaporizer 41.In compressor 10, by driving and make live axle 16 to rotate to live axle 16 as the motor of external drive source etc., thereby rotate swash plate 25 by restriction movable section part 60 it is tilted at several angle, the effect that restriction movable section part 60 plays is that restriction wedge 24 and swash plate 25 relatively rotate with respect to each other.The swing of swash plate 25 is delivered to piston 31 by piston shoes 32, thereby makes piston 31 to-and-fro motion in the cylinder thorax 11a of association.Therefore, extract refrigerant gas from suction chamber 35 and enter compression chamber 33 the cylinder thorax 11a, it is compressed, refrigerant gas is discharged make it enter discharge side 34 then.Regulate by the pressure in inlet air pathway 44, bleed path 45 and 46 pairs of arbor chambeies 15 of displacement control valve,, discharge the refrigerant gas amount (the perhaps discharge capacity of compressor 10) that enters discharge side 34 thereby control from compression chamber 33 to change the inclination angle of swash plate 25.Therefore, obtain and the corresponding cooling effect of compressor 10 discharge capacities by refrigerating circuit 37.
Between compressor 10 on-stream periods, as shown in Figure 7, by piston 31 and piston shoes 32, the compression reaction force P1 and the inhalation power P2 of refrigerant gas are put on swash plate 25, thereby, moment M on swash plate 25, produced, this moment promotes swash plate, so that swash plate 25 is around the intersection revolution of itself and the first imaginary plane CP, thereby, swash plate 25 relative drive shafts 16 are tilted.More specifically, moment M acts on the swash plate 25 by this way, make inhalation power P2 promote swash plate 25 in the first imaginary plane CP suction side, so that it is removed from wedge 24, compression reaction force P1 then promotes to discharge at the first imaginary plane CP swash plate 25 of side, so that it is pressed against on the wedge 24.
Support arm 61 is positioned on the suction side with the guide finge 62 relative first imaginary plane CP, and as the restriction movable section part, acting in conjunction is removed from wedge 24 with restriction swash plate 25.Therefore, restriction movable section part 60 bears a part of moment M, and this part moment M promotes swash plate 25 by inhalation power P2 in the suction side of the relative first imaginary plane CP, and swash plate 25 is removed from wedge 24.
First guide surface 71 and second guide surface 72 as unrestricted movable section part 70, bear a part of moment M, and this part moment M promotes swash plate 25 by compression reaction force P1 on the discharge side of the relative first imaginary plane CP, make swash plate 25 press wedge 24.Promote swash plate 25 so that it from this part moment M that wedge 24 is removed, does not put on unrestricted movable section part 70 by inhalation power P2, make unrestricted movable section part 70 not need to limit swash plate 25 and remove from wedge 24.When compressor 10 at a high speed and when moving under the big discharge capacity, refrigerant gas deficiency in refrigerating circuit 37, thereby therefore the inertial force of piston 31 become very big, thereby, foundation is tending towards further increasing under the state of moment M at swash plate 25 inclination angles, support arm 61 and guide finge 62, the restriction movable section part 60 as movable joint mechanism 26 can bear this moment M.Therefore, compressor 10 can not produce noise that over-tilting caused and the vibration that is surpassed inclination maximum by swash plate 25.That is compressor 10 has reduced noise and generation of vibration in the running.
In the compressor 10 of this preferred implementation, restriction movable section part 60 comprises: support arm 61, and it is arranged on the wedge 24, and has the bullport 61a of band inner peripheral surface; And, guide finge 62, it is arranged on the swash plate 25, and has spherical portion 62a, and spherical portion 62a can slide in bullport 61a.When guide finge 62 was slided in bullport 61a, spherical portion 62a kept level and smooth contacting with the inner peripheral surface of bullport 61a, therefore, and for movable joint mechanism provides good serviceability.(radially) precision of axial precision by guaranteeing bullport 61a and guide finge 62 and the diameter of bullport 61a and spherical portion 62a makes the gap between bullport 61a and the spherical portion 62a less easily.As a result, more can guarantee to reach the above-mentioned advantageous effects that reduces noise and vibration generation.
In the compressor 10 of this preferred implementation, unrestricted movable section part 70 neither limits and does not also need to limit wedge 24 and swash plate 25 relatively rotates with respect to each other.Therefore, except above-mentioned advantageous effects, also reached weight reduction, thereby, the controllability of compressor improved, as response to live axle 16 rotation speed change.
In the compressor 10 of this preferred implementation, unrestricted movable section part 70 comprises: first guide surface 71, and it is arranged on the wedge 24, and towards swash plate 25; And second guide surface 72, it is arranged on the swash plate 25, and towards first guide surface 71.When making unrestricted movable section part 70, have only first guide surface 71 and second guide surface 72 therefore, unrestricted movable section part 70 to be made easily with high-precision processing, thereby, further reduce the cost of production of compressor 10.
In the compressor 10 of this preferred implementation, the 26 relative second false appearance planar S P of movable joint mechanism are positioned at tip position A one side.This makes the top dead center position of piston 31 stable, and irrelevant with the inclination angle of swash plate 25.Therefore, make the volume of compression chamber 33 less, the volume of compression chamber 33 is limited by the head of the piston 31 that is positioned at top dead center position (perhaps going up the gap), thereby, suppress the again expansion of refrigerant gas in compression chamber 33.
In addition, in a preferred embodiment,, the swash plate 25 relative second imaginary plane SP in tip position A side, and are limited moving of suction side relative to the first imaginary plane CP by restriction movable section part 60.By the parallel apparent surface 23 of through hole 22, it moves in the central limit of swash plate 25.But swash plate 25 is then unrestricted around the revolution of straight line O2.When compressor 10 low-speed runnings, in the discharge side of the relative first imaginary plane CP and in the tip position A of relative second imaginary plane SP side, the swash plate 25 of making a concerted effort to put on of compression reaction force and piston 31 inertial force.That is to say, make a concerted effort to promote the adjacent part of swash plate 25 and unrestricted movable section part 70, so that it presses wedge 24, that is, promote second guide surface 72, so that it presses first guide surface 71, therefore, swash plate 25 is supported in firm mode.
When compressor 10 runs up, for instance, when increasing the rotating speed (for example, 4000 to 5000rpm or bigger) of live axle 16, will make a concerted effort to put on swash plate 25 in bottom position B side, the relative second imaginary plane SP, bottom position B is on tip position A opposite.That is to say, make a concerted effort to promote the adjacent part of swash plate 25 and unrestricted movable section part 70, so that it removes from wedge 24, that is, promote second guide surface 72 and remove from first guide surface 71.But swash plate 25 is provided with bearing surface 25a towards the surface of wedge 24, and bearing surface 25a is relative, and the first imaginary plane CP is positioned at the suction side, and the relative second imaginary plane SP is positioned at bottom position B side.When the rotational velocity (for example, 4000 to 5000rpm or bigger) that increases live axle 16, and make swash plate 25 when inclination maximum tilts, make bearing surface 25a press wedge 24.Therefore, the part that swash plate 25 and unrestricted movable section part 70 are adjacent, that is the upper right quarter of straight line O2 shown in swash plate 25 relative Fig. 4 is restricted and does not remove from wedge 24.
Preferably, bearing surface 25a is smaller, as long as but be located in the above-mentioned contact range.If form bearing surface 25a in bigger area, because the deviation in the assembling, bearing surface 25a has only less area reality to contact with wedge 24.In addition, because high-precision processing, larger area bearing surface 25a can make cost of production improve.
In the compressor 10 of preferred implementation, in the counterweight portion of swash plate 25, form bearing surface 25a easily.This helps to reduce cost aborning.
But bearing surface 25a is positioned at the position of itself and wedge 24 contact range, and the power that swash plate 25 is moved, can suitably be born from the axes O 1 of live axle 16 farthest in this position therefore on the direction that causes first guide surface 71 and second guide surface 72 to be moved away from each other.
The compressor 10 of preferred implementation is adapted at using in the vehicle, and live axle 16 continues to be activated when vehicle motor moves.Therefore, compressor 10 turns round under the less discharge capacity of being everlasting.In view of the above, compressor 10 is improving aspect noise abatement and the vibration damping, and this is one of advantageous effects of the present invention.
In the compressor 10 of preferred implementation, swash plate 25 comprises the through hole 22 with parallel apparent surface 23, is used to hold the outer circumferential face of live axle 16.Compare with the situation that axle sleeve is set between live axle 16 and swash plate 25, this has reduced cost of production.The parallel apparent surface 23 of through hole 22 bears a part of moment M, this part moment M promotes swash plate 25 by compression reaction force P1 and inhalation power P2, so that swash plate 25 is around the intersection revolution of itself and the first imaginary plane CP, thereby swash plate 25 relative drive shafts 16 are tilted.Yet as mentioned above, most of moment M is born by restriction movable section part 60 and unrestricted movable section part 70.Therefore, the parallel apparent surface 23 of through hole 22 keeps smoothly contacting with live axle 16, thereby, reduced wearing and tearing therebetween.
Selectively, between swash plate 25 and live axle 16, axle sleeve can be set.The same with movable joint mechanism 26, axle sleeve supports swash plate 25, but makes swash plate 25 relative drive shafts 16 tilt, the same with disclosed in the Japanese patent gazette No.6-123281.Live axle 16 axially, axle sleeve is with respect to the outer circumferential face of live axle 16 also slidably.Axle sleeve bears a part of moment M, and this part moment M promotes swash plate 25, and swash plate 25 is turned round around itself and intersection between the first imaginary plane CP.
Selectively, support arm 61 can be arranged on the swash plate 25, and guide finge 62 then can be arranged on the wedge 24.First guide surface 71 can be arranged on the swash plate 25, and second guide surface 72 then can be arranged on the wedge 24.
Example of the present invention and mode of execution should be regarded explanation as and nonrestrictive, and the present invention is not limited to detailed description given here, but can make amendment in claims institute restricted portion.

Claims (10)

1. displacement-variable swashplate compressor that is used for compressed refrigerant, comprising: shell limits cylinder thorax, arbor chamber, suction chamber and discharge side therein; Piston is contained in the described cylinder thorax in the to-and-fro motion mode, and limits compression chamber in described cylinder thorax; Live axle is driven by external drive source, and is supported by described shell rotary way; Wedge is supported by described live axle in described arbor chamber, so that described wedge is with described drive shaft turns; Swash plate is supported by described live axle in described arbor chamber; Movable joint mechanism is arranged between described wedge and the described swash plate, by described wedge and described movable joint mechanism, makes the described swash plate can be with described drive shaft turns, and can tilt by described relatively live axle, is used for making described reciprocating motion of the pistons by piston shoes; And, steerable control mechanism, in order to control the pressure in the described arbor chamber, thereby by of the to-and-fro motion of described piston based on described swashplate angle, the amount that change enters the described freezing mixture the described discharge side from described compression chamber discharge, it is characterized in that: described movable joint mechanism comprises the restriction movable section part, its relative first imaginary plane is positioned at the suction side, described first imaginary plane comprises the described swash plate tip position corresponding with described piston top dead center position and the axis of described live axle, described restriction movable section part is used to limit described wedge and described swash plate relatively rotates with respect to each other, and limiting described swash plate removes from described wedge, described movable joint mechanism further comprises unrestricted movable section part, its described relatively first imaginary plane is positioned at the discharge side, does not limit described swash plate and removes from described wedge.
2. displacement-variable swashplate compressor according to claim 1, wherein, described restriction movable section part comprises: support arm is arranged on one of described wedge and described swash plate, and has the bullport of band inner peripheral surface; And guide finge, be arranged on in described wedge and the described swash plate another, and have and be used for the spherical portion of sliding at described bullport.
3. displacement-variable swashplate compressor according to claim 1 wherein, is provided with described unrestricted movable section part, so that it does not limit described wedge and described swash plate relatively rotates with respect to each other.
4. displacement-variable swashplate compressor according to claim 3, wherein, described unrestricted movable section part comprises: first guide surface is arranged on one of described wedge and described swash plate another in described wedge and described swash plate; And second guide surface is arranged on in described wedge and the described swash plate another, and towards described first guide surface, described second guide surface can contact with described first guide surface.
5. displacement-variable swashplate compressor according to claim 1, wherein, relative second imaginary plane of described movable joint mechanism is positioned at the tip position side of described swash plate, described second imaginary plane comprises the axis of described live axle, and it is perpendicular with described first imaginary plane, described swash plate is provided with bearing surface towards the surface of described wedge, described relatively first imaginary plane of described bearing surface is positioned at the suction side, and described relatively second imaginary plane is positioned at the opposite side of described tip position, when making described swash plate when inclination maximum tilts, described bearing surface contacts with described wedge, thereby limits the described inclination maximum of described swash plate.
6. displacement-variable swashplate compressor according to claim 5 wherein, forms described bearing surface in the counterweight portion in being arranged at described swash plate.
7. displacement-variable swashplate compressor according to claim 5, wherein, make described bearing surface be positioned at described bearing surface can with the position of described wedge contact range, this position is from the axis of described live axle farthest.
8. displacement-variable swashplate compressor according to claim 1 wherein, when described external drive source is moved, continues described live axle is driven.
9. displacement-variable swashplate compressor according to claim 1, wherein, described swash plate has the through hole with parallel apparent surface, is used to hold the outer circumferential face of described live axle.
10. displacement-variable swashplate compressor according to claim 1, wherein, described control mechanism comprises: inlet air pathway is used to connect described discharge side and described arbor chamber; The path of bleeding is used to connect described arbor chamber and described suction chamber; And displacement control valve is arranged in the described inlet air pathway.
CNA2006100587815A 2005-03-04 2006-03-03 Swash plate type variable displacement compressor Pending CN1828052A (en)

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