CN103459846A - Swash-plate-type compressor - Google Patents
Swash-plate-type compressor Download PDFInfo
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- CN103459846A CN103459846A CN2012800149814A CN201280014981A CN103459846A CN 103459846 A CN103459846 A CN 103459846A CN 2012800149814 A CN2012800149814 A CN 2012800149814A CN 201280014981 A CN201280014981 A CN 201280014981A CN 103459846 A CN103459846 A CN 103459846A
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- chamber
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- suction chamber
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- cylinder bores
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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
- F04B27/0804—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 rotary cylinder block
- F04B27/0821—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication
- F04B27/0839—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication valve means, e.g. valve plate
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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
- F04B27/1009—Distribution members
- F04B27/1018—Cylindrical distribution members
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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
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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
- 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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A swash-plate-type compressor (10) of a double-headed-piston configuration, wherein: a front intake chamber (17) is formed set apart from a swash plate chamber (25) so as to be positioned in a narrow space between circumferentially arranged front cylinder bores (28); and an intake-chamber-communication path (50a) is formed in a cylinder block (11), the intake-chamber-communication path allowing the front intake chamber (17) and a shaft hole (11a) to communicate. A front-bore-communication path (50b) is formed on the cylinder block (11), the communication path allowing each of the plurality of front cylinder bores (28) to communicate with the shaft hole (11a). A front rotary valve (RF) is provided on a rotating shaft (22) in which a lead-in groove (22a) is formed. The lead-in groove allows the intake-chamber communication path (50a) and the front-bore communication path (50b) to communicate in the stated order, while the lead-in groove rotates integrally with the rotating shaft (22). Provided thereby is a compact swash-plate-type compressor in which any decrease in pulsation or intake efficiency is minimized.
Description
Technical field
The present invention relates to be formed with for running shaft and insert logical axis hole and form and insert for piston respectively the oblique tray type compressor of logical a plurality of cylinder bores around axis hole in the mode in circumferential array at cylinder block.
Background technique
As this oblique tray type compressor, exist and adopted the double-headed piston type oblique tray type compressor of double-head piston as piston, for example, can be set forth in disclosed device in patent documentation 1.As shown in figure 11, in the oblique tray type compressor 80 of patent documentation 1, at cylinder block 81, be formed with three cylinder bores 81a, and taken in double-head piston 82 in each cylinder bores 81a.In addition, in cylinder block 81, suction chamber 83 forms in the mode in the gap that is positioned at two adjacent cylinder bores 81a, and discharge chamber 84 forms in the mode in the gap that is positioned at other adjacent cylinder bores 81a.And, gap by the cylinder bores 81a by adjacent effectively utilizes in formation suction chamber 83 and discharge chamber 84, thereby will guarantee that the suction chamber 83 of necessary capacity and discharge chamber 84 are accommodated in cylinder block 81 in order to suppress pulsation, suppress the maximization of oblique tray type compressor 80 builds.
Yet though, not shown, in the oblique tray type compressor 80 of patent documentation 1, sucking refrigeration agent from suction chamber to cylinder bores 81a is to open suction port by the suction valve of leaf valve type to carry out.In the suction that has used above-mentioned suction valve, exist suction valve based in cylinder bores 81a and the pressure difference between suction chamber opened and closed, pressure drop in cylinder bores 81a is just opened suction valve to the pressure of regulation, and can not open on desirable opportunity the situation of suction valve, thereby the worry that exists suction efficiency to worsen.
Therefore, for the disclosed oblique tray type compressor 80 of the patent documentation 1 of the maximization that has suppressed build, in order to prevent the deterioration of suction efficiency, and effectively adopt the rotary valve that cylinder bores mechanically is communicated with suction chamber.
Patent documentation 1: Japanese kokai publication hei 9-317633 communique
Patent documentation 2: TOHKEMY 2007-138925 communique
Patent documentation 3: TOHKEMY 2007-270790 communique
As shown in figure 12, in the disclosed oblique tray type compressor 90 of patent documentation 2 of the compressor as having adopted rotary valve, make the accommodation chamber 93a(suction chambers of refrigeration agent via connectivity slot 98 99 temporary transient arrival front casing 93 sides from the swash plate chamber).Therefore, for refrigeration agent being imported to the suction path 96 be communicated with cylinder bores 97, and pass through supply passage 92a by the refrigeration agent of front casing 93 sides (accommodation chamber 93a) guiding cylinder block 91 sides.That is, must form at running shaft 92 the supply passage 92a that always extends to cylinder block 91 from front casing 93, thereby make supply passage 92a elongated vertically.Therefore, in the oblique tray type compressor 90 of patent documentation 2, owing to forming supply passage 92a, and the build of oblique tray type compressor 90 is maximized vertically.
As shown in figure 13, in the disclosed oblique tray type compressor 100 of patent documentation 3 of the compressor as having adopted equally rotary valve, be formed with supply passage 102 in running shaft 101, and be formed with and make in supply passage 102 and the outer introduction hole 101a be communicated with of running shaft 101.In cylinder block 104, be formed with and suck recess 105 around running shaft 101, and introduction hole 101a can be communicated with swash plate chamber 106 via sucking recess 105 with supply passage 102.
And, in patent documentation 3, if suction recess 105 and introduction hole 101a are communicated with swash plate chamber 106, the refrigeration agent of swash plate chamber 106 is imported into supply passage 102 from sucking recess 105 via introduction hole 101a, and, from supply passage 102, via rotary valve 107, be imported into cylinder bores 108.In patent documentation 3, form introduction hole 101a at running shaft 101, thereby running shaft 101 is elongated vertically, and forms and suck recess 105 at cylinder block 104, thereby the build of oblique tray type compressor 100 maximizes vertically.In addition, for supply passage 102, in order to ensure the intensity of running shaft 101, need to make the large footpath of running shaft 101, its result causes the build of oblique tray type compressor 100 radially to maximize.
Like this, the oblique tray type compressor 90,100 that has adopted existing rotary valve 99,106 is kept intact the swash plate chamber as suction chamber, so the shape of rotary valve 107 becomes complicated, large-scale, and result causes the build of oblique tray type compressor 90,100 to maximize.
Summary of the invention
The object of the present invention is to provide and suppress pulsation and the reduction of suction efficiency and small-sized oblique tray type compressor.
To achieve these goals, the oblique tray type compressor of a mode of the present invention possesses: cylinder block, swash plate, a plurality of piston, running shaft and rotary valve.The said cylinder body has: axis hole, a plurality of cylinder bores, swash plate chamber and suction chamber.Above-mentioned axis hole extends in the mode that connects the said cylinder body.Above-mentioned a plurality of cylinder bores around above-mentioned axis hole along circumferential array.Above-mentioned suction chamber arranges discretely in gap and the above-mentioned swash plate chamber of adjacent cylinder bores.Above-mentioned swash plate is incorporated in above-mentioned swash plate chamber.Above-mentioned a plurality of piston is connected with above-mentioned swash plate and is inserted through respectively above-mentioned a plurality of cylinder bores.Above-mentioned running shaft is inserted through above-mentioned axis hole and rotates with above-mentioned swash plate one.Above-mentioned rotary valve is arranged at this running shaft in the mode with above-mentioned running shaft one rotation.The said cylinder body has access and a plurality of cylinder bores access for suction chamber that above-mentioned suction chamber is communicated with above-mentioned axis hole.Above-mentioned a plurality of cylinder bores is communicated with respectively above-mentioned a plurality of cylinder bores with path individually with above-mentioned axis hole.Thereby above-mentioned rotary valve makes above-mentioned suction chamber be communicated with successively with access with above-mentioned a plurality of cylinder bores with access with above-mentioned running shaft one rotation.
Accordingly, in cylinder block, suction chamber and cylinder bores centered by rotary valve in circumferential array.Its result, even adopt rotary valve in suction, the build that also can not make rotary valve and oblique tray type compressor is axially, radially maximize.And, as suction, adopted rotary valve rather than suction valve, with suction valve, compare, can also prevent the deterioration of suction efficiency.
Preferred above-mentioned suction chamber comprises a plurality of suction chambers that lay respectively at the gap of adjacent cylinder bores.Above-mentioned suction chamber comprises a plurality of suction chamber access that above-mentioned a plurality of suction chamber is communicated with above-mentioned axis hole respectively individually with access.
Accordingly, in cylinder block, suction chamber and cylinder bores centered by rotary valve alternately in circumferential array.Therefore, in order to make cylinder bores by rotary valve, with suction chamber, be communicated with, as long as only supply passage is formed to the shape of extending along the circumferential part of rotary valve.Therefore, can make to be formed at the shape simplification of the rotary valve of running shaft, thereby can further shorten length vertically.
Preferably the said cylinder body has a plurality of discharge chambers that lay respectively at the gap of adjacent cylinder bores.
Accordingly, though cylinder block because of the refrigeration agent thermal expansion of the high temperature that is expelled to discharge chamber, the thermal expansion position also can be distributed in equably shell circumferentially.Its result, can reduce the impact of each cylinder bores and piston expanded by heating.
Preferably above-mentioned a plurality of discharge chambers in the radial arrangement of said cylinder body in the outside of above-mentioned suction chamber.
Preferably the said cylinder body has the suction port connected for outside pipe arrangement and the suction path that above-mentioned suction port is communicated with above-mentioned suction chamber, and above-mentioned suction channel setting is for to separate with above-mentioned swash plate chamber.
Accordingly, although have the running shaft of rotary valve, because of the sliding friction that is accompanied by rotation, generate heat, refrigeration agent is from the suction port to the suction chamber, further in the suction path of the refrigeration agent of cylinder bores, only by rotary valve the time and running shaft carry out heat exchange.And rotary valve shorten length vertically, therefore can be rotated the valve heating by ultimate attainment inhibition refrigeration agent, thereby improve suction efficiency.
With access, the recess by the inwall that is formed at above-mentioned axis hole forms preferred above-mentioned suction chamber, and this recess has the opening end be communicated with above-mentioned swash plate chamber.Configure thrust-bearing between the opening end of above-mentioned swash plate and above-mentioned recess, above-mentioned thrust-bearing is by the opening end obturation of above-mentioned recess.
Accordingly, when cast block, can form the suction chamber access simultaneously.Therefore, need to be by the cutting suction chambers such as drill bit access after cast block, thus can save the man-hour of making cylinder block.
Preferably, above-mentioned suction chamber consists of the first recess and the second recess with access, above-mentioned the first recess is formed at the inwall of above-mentioned suction chamber and has the opening end at the axial end face opening of said cylinder body, and above-mentioned the second recess is formed at the inwall of above-mentioned axis hole and has the opening end be communicated with above-mentioned swash plate chamber.Configure thrust-bearing between the opening end of above-mentioned swash plate and above-mentioned the second recess, above-mentioned thrust-bearing is by the opening end obturation of above-mentioned the second recess.
Accordingly, when cast block, not only can form the suction chamber access simultaneously, also can make the opening miniaturization of suction chamber with access and swash plate chamber, therefore can make the thrust-bearing miniaturization as inaccessible parts.
Preferably above-mentioned a plurality of cylinder bores are three cylinder bores.
Accordingly, in cylinder block, can guarantee that the capacity of cylinder bores is larger, thereby can further reduce pulsation.
According to the present invention, can provide the small-sized oblique tray type compressor that suppresses pulsation and suction efficiency reduction.
The accompanying drawing explanation
Fig. 1 means the sectional view of the line of the 1-1 along Fig. 3 of the double-headed piston type oblique tray type compressor of the first mode of execution of the present invention.
Fig. 2 means the sectional view of the line of the 2-2 along Fig. 3 of the double-headed piston type oblique tray type compressor of the first mode of execution.
Fig. 3 means the sectional view of the line of the 3-3 along Fig. 1 of front side discharge chamber and front side suction chamber.
Fig. 4 means the sectional view of the line of the 4-4 along Fig. 1 of front side cylinder bores, front side suction chamber and front side discharge chamber.
Fig. 5 means the partial sectional view of the double-headed piston type oblique tray type compressor of the second mode of execution of the present invention.
Fig. 6 means the rotary valve of Fig. 5 and the unfolded drawing in axis hole.
Fig. 7 (a) is in the past the enter the room sectional view of the line of the 7a-7a along Fig. 5 of cylinder block of side presentation graphs 5 of side draught, and Fig. 7 (b) means the sectional view of the line of the 7b-7b along Fig. 5 of cylinder block from the axis hole side.
Fig. 8 means the partial sectional view of the double-headed piston type oblique tray type compressor of other examples.
Fig. 9 means the sectional view of the double-headed piston type oblique tray type compressor of other examples.
Figure 10 means the unfolded drawing of the front side rotary valve of other examples.
Figure 11 means the figure of patent documentation 1.
Figure 12 means the figure of patent documentation 2.
Figure 13 means the figure of patent documentation 3.
Embodiment
(the first mode of execution)
Below, according to Fig. 1～Fig. 4, the first mode of execution that oblique tray type compressor of the present invention is embodied in to double-headed piston type oblique tray type compressor 10 is described.
As shown in Figure 1 and Figure 2, below double-headed piston type oblique tray type compressor 10(, only be recited as compressor 10) shell H in, cylinder block 11 in engaged a pair of cylinder block 11,12, front side (being left side at Fig. 1) engages front casing 13 is arranged via front side valve port organizator (front valve/port formation body) 15.In addition, the cylinder block 12 at rear side (being right side in Fig. 1) engages rear casing 14 is arranged via rear side valve port organizator 16.And, a pair of cylinder block 11,12 of shell H sandwiched between front casing 13 and rear casing 14 and forming.
Insert and be connected with running shaft 22 being formed through in axis hole 11a, the 12a of cylinder block 11,12, and, this running shaft 22 be formed on axis hole 11a, 12a inner peripheral surface sealing material week surface bearing for rotating.In addition, running shaft 22 is to run through slotting the leading to of mode at inserting hole 15d, the 16d of front side valve port organizator 15 and central authorities' formation of side valve port organizator 16 afterwards.At the running shaft 22 outstanding protruding terminus of side valve port organizator 15 in the past, the inner peripheral surface of front casing 13 and and the side face of the opposed running shaft 22 of this inner peripheral surface between by the gland seal device 23 of lip seal type, hermetic sealed.Gland seal device 23 is accommodated between the side face of the inner peripheral surface of front casing 13 and running shaft 22 and is divided in the accommodation chamber 13c formed.
In addition, be fixed with at running shaft 22 swash plate 24 rotated with this running shaft 22 one.Swash plate 24 is positioned at the inboard of cylinder block 11,12, and is accommodated in the swash plate chamber 25 that is divided formation between cylinder block 11,12.Be folded with thrust-bearing 26 between the circular base portion 24a of the end face of the cylinder block 11 of front side and swash plate 24.Be folded with thrust-bearing 27 between the base portion 24a of the end face of the cylinder block 12 of rear side and swash plate 24.Thrust-bearing 26,27 clips swash plate 24 and limits the movement of this swash plate 24 along the central axis L direction of running shaft 22, and thrust-bearing 26,27 is pressed against respectively the axis hole 11a in cylinder block 11,12, the open end of 12a.
As shown in Figure 4, the cylinder block 11 in front side is arranged with three front side cylinder bores 28 in the mode of surrounding running shaft 22 around running shaft 22.In addition, as shown in Figure 1, at the cylinder block 12 of rear side, in the mode of surrounding running shaft 22, around running shaft 22, be arranged with three rear side cylinder bores 29.Axial (fore-and-aft direction) that front side cylinder bores 28 and rear side cylinder bores 29 are extended in central axis L forms a pair of, and inserts and be connected with the double-head piston 30 as piston in two cylinder bores 28,29.And front side cylinder bores 28 is by front side valve port organizator 15 and double-head piston 30 obturations, and rear side cylinder bores 29 is by rear side valve port organizator 16 and double-head piston 30 obturations.
Be passed to double-head piston 30 with the rotatablely moving of swash plate 24 of running shaft 22 one rotations via a pair of crawler shoe 31 arranged across swash plate 24, thereby double-head piston 30 is in front side cylinder bores 28 and rear side cylinder bores 29 is interior moves back and forth along front and back.And, in front side cylinder bores 28, front side pressing chamber 28a is divided by double-head piston 30 and front side valve port organizator 15, and, in rear side cylinder bores 29, rear side pressing chamber 29a is divided by double-head piston 30 and rear side valve port organizator 16.
In front casing 13 and cylinder block 11, in the mode of surrounding running shaft 22 and the front side valve port organizator 15 of perforation, be formed with three front side suction chambers 17.As shown in Figure 4, three front side suction chambers 17 are circumferentially respectively disposing one in the gap of adjacent front side cylinder bores 28 around axis hole 11a edge.And three front side suction chambers 17 are disposed at the outer circumferential side of axis hole 11a in the mode that separates equal intervals.
In addition, as shown in Figure 1 and Figure 2, the axial length along running shaft 22 of other two front side suction chambers 17 of the axial Length Ratio along running shaft 22 in three front side suction chambers 17, a front side suction chamber 17 is longer, thereby volume is larger.In addition, as shown in Figure 3, in front casing 13, three front side suction chambers 17 are communicated with accommodation chamber 13c respectively, and three front side suction chambers 17 are interconnected centered by accommodation chamber 13c, thereby become a continuous space.
As shown in Figure 1 and Figure 3, divided front side discharge chamber 28b in the mode of surrounding running shaft 22 between front casing 13 and front side valve port organizator 15.Front side discharge chamber 28b is for the space of discharging from the refrigeration agent of three front side pressing chamber 28a, at the outer circumferential side of front casing 13, is divided into ring-type.
In the discharge chamber 28b of this front side, and via the opposed position of pressing chamber 28a, each front side opening of front side valve port organizator 15.And, in the discharge chamber 28b of front side, be communicated with path each other with the opposed space of pressing chamber 28a, each front side, thereby become a continuous space.
As shown in Figure 3 and 4, be formed with at three places of cylinder block 11 the front side discharge chamber 40 be communicated with front side discharge chamber 28b.This front side discharge chamber 40 connects front side valve port organizator 15 and extends the cylinder block 11 to front side.The front side discharge chamber 40 that is formed at three places be arranged in running shaft 22 around, and respectively be formed with one in the gap of the circumferential adjacent front side cylinder bores 28 of axis hole 11a.In addition, each front side discharge chamber 40 is formed in the outside of front side suction chamber 17 in the radial shape of cylinder block 11.
As shown in Figure 1 and Figure 3, in the position corresponding with each front side cylinder bores 28 of front side valve port organizator 15, be formed with tap hole 15a, and be formed with expulsion valve 15b in the position corresponding with this tap hole 15a.And, at front side valve port organizator 15, be formed with the retainer 15c that the aperture to expulsion valve 15b is limited.
Next, the structure of rear side described.
As shown in Figure 1 and Figure 2, on rear casing 14 and cylinder block 12, three rear side suction chambers 18 are arranged in running shaft 22(axis hole 12a) around and connect after side valve port organizator 16 and forming.Identical with front side, three rear side suction chambers 18 respectively dispose one in the gap of the circumferential adjacent rear side cylinder bores 29 along axis hole 12a.In addition, the axial length along running shaft 22 of other two rear side suction chambers 18 of the axial Length Ratio along running shaft 22 of a rear side suction chamber 18 in three rear side suction chambers 18 is longer, thereby volume is larger.
In addition, divide and have the rear casing side draught to enter the room 19 between the central authorities of rear casing 14 and rear side valve port organizator 16.Enter the room and 19 be communicated with 18, three rear side suction chambers 18 of three rear side suction chambers and enter the room centered by 19 and become a continuous integral body by this rear casing side draught at this rear casing side draught.And front side suction chamber 17 configures one by one to form a pair of mode with the fore-and-aft direction that rear side suction chamber 18 extends in central axis L.In addition, be formed with front side suction chamber 17 and rear side suction chamber 18 in the mode that clips swash plate 24 in cylinder block 11,12.
Divided in the form of a ring rear side discharge chamber 29b in the mode of surrounding running shaft 22 between rear casing 14 and rear side valve port organizator 16.Rear side discharge chamber 29b is for the space of discharging from the refrigeration agent of three rear side pressing chamber 29a, at enter the room 19 outer circumferential side of rear casing side draught, is divided.In this rear side discharge chamber 29b, and via each opposed position of rear side cylinder bores 29 of rear side valve port organizator 16 size openings identical with the circle with rear side pressing chamber 29a.In addition, in rear side discharge chamber 29b, be communicated with by path each other with each opposed space of rear side cylinder bores 29, thereby become a continuous space.
Be formed with the rear side discharge chamber 42 be communicated with rear side discharge chamber 29b at three places of cylinder block 12.This rear side discharge chamber 42 side valve port organizator 16 extend the cylinder block 12 to rear side from rear casing 14 connects.The rear side discharge chamber 42 that is formed at three places be arranged in axis hole 12a around, and respectively be formed with one in the gap of the circumferential adjacent rear side cylinder bores 29 along axis hole 12a.In addition, each rear side discharge chamber 42 is formed in the outside of rear side suction chamber 18 in the radial shape of cylinder block 12.And the fore-and-aft direction that front side discharge chamber 28b and rear side discharge chamber 29b extend in central axis L configures to form one by one a pair of mode.
As shown in Figure 1, be formed with tap hole 16a in the position corresponding with each rear side discharge chamber 29b of rear side valve port organizator 16, and be formed with expulsion valve 16b in the position corresponding with this tap hole 16a.And, at rear side valve port organizator 16, be formed with the retainer 16c that the aperture to expulsion valve 16b is limited.
Be formed with and suck path 43 at cylinder block 11,12, and this opening that sucks the front side of path 43 is communicated with the front side suction chamber 17 of volume maximum in three front side suction chambers 17, the opening of rear side is communicated with the rear side suction chamber 18 of volume maximum in three rear side suction chambers 18.And, at the cylinder block 11 of front side, be formed with suction port 44.One end of this suction port 44 is at the outer circumferential face opening of cylinder block 11, and the other end is at the inner peripheral surface opening that sucks path 43.And, be connected with the outside pipe arrangement 32 in the external refrigerant loop of the outside that is equipped on compressor 10 at an end opening of suction port 44.In addition, suck path 43 and be formed in cylinder block 11,12, thereby separate with swash plate chamber 25.
In addition, suction path 43 forms the suction chamber 17,18 in front side and rear side volume maximum is communicated with each other.Therefore, sucking path 43 is formed at the front side discharge chamber 40 of the outer circumferential side that is positioned at above-mentioned suction chamber 17 and is positioned at the position that the rear side discharge chamber 42 of the outer circumferential side of above-mentioned suction chamber 18 is axially clipping.
In addition, as shown in Figure 2, at cylinder block 11,12, be formed with drain passageway 45, and the opening of the front side of this drain passageway 45 is communicated with in three front side discharge chambers 40 one, the opening of rear side is communicated with in three rear side discharge chambers 42 one.And, at cylinder block 11, be formed with exhaust port 46.One end of this exhaust port 46 is at the outer circumferential face opening of cylinder block 11, and the other end is at the inner peripheral surface opening of drain passageway 45.And, be connected with the outside pipe arrangement 33 in the external refrigerant loop of the outside that is equipped on compressor 10 at exhaust port 46.
In addition, as shown in Figure 3, drain passageway 45 is formed at the position of circumferentially staggering towards cylinder block 11,12, position from being formed with above-mentioned suction path 43 in cylinder block 11,12.Particularly, for front side discharge chamber 40 and rear side discharge chamber 42 axially clipping suction path 43, in the front side discharge chamber 40 by circumferentially staggering and rear side discharge chamber 42, in the position axially clipped, be formed with drain passageway 45.
In the situation that use compressor 10 to form the refrigeration cycle that vehicle air conditioning is used, the external refrigerant loop is connected the exhaust port of compressor 10 46 via outside pipe arrangement 32,33 with suction port 44.And the external refrigerant loop has condenser (condensing), expansion valve (expansion valve) and vaporizer (evaporator), above-mentioned parts externally configure from the exhaust port 46 of compressor 10 on refrigerant circuit in order.
Next, the structure of the suction in compressor 10 is described.
At first, the suction structure of front side described.As shown in Figure 4, be formed with respectively at cylinder block 11 the suction chamber access 50a that each front side suction chamber 17 is communicated with axis hole 11a.This suction chamber uses the end of access 50a at front side suction chamber 17 openings, and the other end is in the sealing material side face upper shed of axis hole 11a.In addition, suction chamber is radially inclination and the extension slightly along cylinder block 11 with access 50a, thereby is formed in cylinder block 11.
Be formed with respectively the front side cylinder bores access 50b that axis hole 11a is communicated with each front side cylinder bores 28 at cylinder block 11.The sealing material side face upper shed of the end of access 50b at axis hole 11a of this front side cylinder bores, and the other end is at front side cylinder bores 28 openings.And suction chamber alternately is disposed at the circumferential of axis hole 11a by access 50a and front side cylinder bores with access 50b.
As shown in Fig. 1 and Fig. 4, the side face in the front side of running shaft 22 is formed with lead-in groove 22a.This lead-in groove 22a is arranged with in the side face of front casing 13 sides of the running shaft 22 as solid shaft.Lead-in groove 22a is towards the sealing material side face opening of axis hole 11a, and can by access 50a and front side cylinder bores, with access 50b, be communicated with individually with suction chamber.And the position of lead-in groove 22a is accompanied by the rotation of running shaft 22 and changes, thus suction chamber access 50a and front side cylinder bores access 50b that mechanically switching is communicated with for lead-in groove 22a.
The front side rotary valve RF that the part of the running shaft 22 therefore, surrounded by the sealing material side face becomes one and is formed at running shaft 22.In addition, lead-in groove 22a makes a suction chamber be interconnected with access 50b with the circumferential adjacent front side cylinder bores at axis hole 11a with access 50a.And suction chamber is communicated with by the rotation of running shaft 22 and via lead-in groove 22a with access 50b with the front side cylinder bores individually with access 50a, thereby by the in the past side draught adjacent front side cylinder bores 28 of 17 suctions of entering the room of refrigeration agent.Therefore, in the present embodiment, lead-in groove 22a becomes the supply passage that utilizes front side rotary valve RF that front side cylinder bores 28 is communicated with front side suction chamber 17.
Next, the suction structure of rear side described.
As shown in Figure 1 and Figure 2, be formed with respectively at cylinder block 12 rear side that each rear side cylinder bores 29 is communicated with axis hole 12a and import path 51.This rear side imports an end of path 51 at each rear side cylinder bores 29 openings, and the other end is in the sealing material side face upper shed of axis hole 12a.In addition, be formed with and supply with road 22b at the side face of the rear side of running shaft 22.The rear casing side draught of an end in rear casing 14 of this supply road 22b 19 openings of entering the room.In addition, supplying with the distolateral the other end that can import path 51 with rear side of another of road 22b is communicated with.And, supply with 22b position, road and be accompanied by the rotation of running shaft 22 and change, thereby mechanically the rear side importing path 51 that road 22b is communicated with is supplied with in switching.Therefore, the rear side rotary valve RR that the part of sealed material side face encirclement running shaft 22 becomes one and is formed at running shaft 22.
Next, the effect of the compressor 10 of said structure described.
Then, refrigeration agent is sucked into and sucks path 43 via suction port 44, thereby refrigeration agent is supplied to each front side suction chamber 17 and each rear side suction chamber 18.And, if front side cylinder bores 28 moves to suction stroke, as shown in Figure 4, a suction chamber is communicated with via the lead-in groove 22a of front side rotary valve RF with access 50b by access 50a and the front side cylinder bores adjacent with access 50a with this suction chamber.So refrigeration agent in the past side draught is entered the room and 17 via front side rotary valve RF, is inhaled into front side cylinder bores 28.
And, lead-in groove 22a is accompanied by the rotation of running shaft 22 and becomes and is communicated with access 50a is non-with suction chamber, thereby remove suction chamber and use access 50a and front side cylinder bores being communicated with access 50b, if and cut off front side cylinder bores 28, front side cylinder bores 28 moves to compression stroke and discharges stroke.So the refrigeration agent in the pressing chamber 28a of front side is pushed expulsion valve 15b open and is discharged to front side discharge chamber 28b from tap hole 15a.And the refrigeration agent that is expelled to front side discharge chamber 28b flows out to the external refrigerant loop from front side discharge chamber 40 by drain passageway 45 and exhaust port 46.
On the other hand, at rear side, under the state of shell side suction chamber 19 supply system cryogens backward, if rear side cylinder bores 29 moves to suction stroke,, at rear side rotary valve RR and the rear casing side draught 19 supply road 22b that are communicated with that enter the room, import paths 51 with one or two rear sides and be communicated with.So, refrigeration agent from the rear casing side draught enter the room 19 via rotary valve RR be supplied to this rear side and import path 51, thereby refrigeration agent is inhaled into this rear side and imports the rear side cylinder bores 29 that path 51 is communicated with.
And, supplying with road 22b is accompanied by the rotation of running shaft 22 and becomes and import with rear side that path 51 is non-to be communicated with, import path 51 and rear casing side draught and enter the room 19 be communicated with thereby remove rear side, and if cut off rear side cylinder bores 29, rear side cylinder bores 29 moves to compression stroke and discharge stroke.So the refrigeration agent in rear side pressing chamber 29a is pushed expulsion valve 16b open and is discharged to rear side discharge chamber 29b from tap hole 16a.And the refrigeration agent that is expelled to rear side discharge chamber 29b flows out to the external refrigerant loop from rear side discharge chamber 42 by drain passageway 45 and exhaust port 46.
Therefore, according to present embodiment, can obtain following such advantage.
(1), in double-headed piston type oblique tray type compressor 10, be formed with three front side cylinder bores 28 around the axis hole 11a in cylinder block 11, and respectively dispose a front side suction chamber 17 in the gap of adjacent front side cylinder bores 28.That is, alternately configure front side cylinder bores 28 and front side suction chamber 17 around axis hole 11a.In addition, form access 50a and front side cylinder bores access 50b that front side cylinder bores 28 is communicated with axis hole 11a for suction chamber that each front side suction chamber 17 is communicated with axis hole 11a at cylinder block 11, and circumferentially alternately configure suction chamber use access 50a and front side cylinder bores access 50b at axis hole 11a.And the refrigeration agent of each front side suction chamber 17 after directly being directed into lead-in groove 22a, is inhaled into front side cylinder bores 28 via the front side cylinder bores with access 50b with access 50a at the suction chamber via in cylinder block 11.Therefore, in order to utilize front side rotary valve RF, make to be communicated with front side suction chamber 17 in circumferential adjacent front side cylinder bores 28, as long as lead-in groove 22a is formed to the shape of extending along the circumferential part of rotary valve RF.Therefore, the shape of front side rotary valve RF can be simplified, therefore front side rotary valve RF length vertically can be shortened.Its result, adopt front side rotary valve RF even if possess in cylinder block 11 in the suction of compressor 10 of front side suction chamber 17, and the build of compressor 10 also is difficult to axially, radially maximize.And, as suction, adopt rotary valve rather than suction valve, front side cylinder bores 28 mechanically is communicated with front side suction chamber 17, therefore with suction valve, compare the deterioration that can also prevent suction efficiency.In addition, at cylinder block 11, be formed with three front side suction chambers 17, therefore can fully guarantee the volume of suction chamber, thereby can suppress pulsation.
(2) respectively be formed with a front side suction chamber 17 in the gap of the circumferential adjacent front side cylinder bores 28 of axis hole 11a.In addition, be formed with at cylinder block 11 the suction chamber access 50a that each front side suction chamber 17 is communicated with the lead-in groove 22a of front side rotary valve RF.And, the refrigeration agent of each front side suction chamber 17 directly can be directed into to lead-in groove 22a via suction chamber with access 50a.Therefore, do not need refrigeration agent is temporarily imported the suction nip territory of front casing 13, therefore need to not form the lead-in groove 22a that extends to cylinder block 11 from front casing 13 at running shaft 22.Therefore, running shaft 22 in the axial front and back of lead-in groove 22a by axis hole 11a(sealing material side face) supporting, thereby guarantee the bearing area of running shaft 22, and then can improve abrasion resistance.
(3) identical with front side suction chamber 17, respectively be formed with a rear side suction chamber 18 in the mode of surrounding running shaft 22 in the gap of adjacent rear side cylinder bores 29.Therefore, front side suction chamber 17 and rear side suction chamber 18 are arranged at cylinder block 11,12 radially, thereby can suppress the build maximization vertically of compressor 10.
(4) be formed with front side discharge chamber 28b at front casing 13, at rear casing 14, be formed with rear side discharge chamber 29b, and be communicated with three front side discharge chambers 40 at front side discharge chamber 28b, at rear side discharge chamber 29b, be communicated with three rear side discharge chambers 42.And each discharge chamber 40,42 respectively disposes one in the gap of adjacent cylinder bores 28,29.Therefore, in cylinder block 11,12, can guarantee that the capacity of each discharge chamber 40,42 is larger, thereby can further reduce pulsation.
(5) each discharge chamber 40,42 in the radial arrangement of cylinder block 11,12 in the outside of each suction chamber 17,18.Therefore, though cylinder block 11,12 because of the refrigeration agent thermal expansion of the high temperature that is expelled to each discharge chamber 40,42, the thermal expansion position also can be distributed in cylinder block 11,12 radially equably.Its result, can reduce the impact that double-head piston 30 is subject to the thermal distortion of each cylinder bores 28,29.
(6) each discharge chamber 40,42 respectively disposes one in the gap of each cylinder bores 28,29.Therefore, though cylinder block 11,12 because of the refrigeration agent thermal expansion of the high temperature that is expelled to each discharge chamber 40,42, the thermal expansion position also can be distributed in equably cylinder block 11,12 circumferentially.Its result, can reduce the impact that double-head piston 30 is subject to the thermal distortion of each cylinder bores 28,29.
(7) be formed with suction port 44 at cylinder block 11, and be formed with at cylinder block 11,12 the suction path 43 be communicated with front side suction chamber 17 and rear side suction chamber 18.Therefore, refrigeration agent is being sucked to each suction chamber 17,18 o'clock, refrigeration agent can be via swash plate chamber 25.Therefore, can prevent from being inhaled into the refrigeration agent of each suction chamber 17,18 because of the gas leakage of the high temperature of inflow swash plate chamber 25, the heated situation of running shaft 22 that sliding friction is generated heat.
(8) front side suction chamber 17 and rear side suction chamber 18 are a pair of in axial formation, and front side discharge chamber 40 is also a pair of in axial formation with rear side discharge chamber 42.In addition, adopt front side rotary valve RF as the suction that sucks front side cylinder bores 28, adopt rear side rotary valve RR as the suction that sucks rear side cylinder bores 29.Therefore, at front side and rear side, suck structure identical, therefore can suppress the vibration caused by the different of the suction structure of front side and rear side, the situation of generation abnormal sound.
(9) respectively be formed with a front side suction chamber 17 in the mode of surrounding axis hole 11a in the gap of circumferentially adjacent front side cylinder bores 28.In addition, be formed with access 50a and front side cylinder bores access 50b that lead-in groove 22a is communicated with front side cylinder bores 28 for suction chamber that each front side suction chamber 17 is communicated with the lead-in groove 22a of front side rotary valve RF at cylinder block 11.And, the refrigeration agent that can make each front side suction chamber 17 sucks front side cylinder bores 28 via access 50a, lead-in groove 22a and front side cylinder bores for suction chamber with access 50b, thereby can in cylinder block 11, complete the enter the room suction action of 17 refrigeration agents to front side cylinder bores 28 of side draught in the past.Therefore, if compare with the situation that sucks front side cylinder bores 28 via the groove that extends in front casing 13, swash plate chamber 25 is interior, can shorten the contact area of refrigeration agent and lead-in groove 22a.Its result, can reduce the contact area growth that is accompanied by refrigeration agent and lead-in groove 22a and the overheated increase of suction brought, thereby can prevent the deterioration of suction efficiency.
(10) though running shaft 22 because of the sliding friction with axis hole 11a, 12a etc., generate heat, but from suction port 44 until front side suction chamber 17, further until in the suction path of the refrigeration agent of front side cylinder bores 28, refrigeration agent, by lead-in groove 22a the time, carries out heat exchange via front side rotary valve RF and running shaft 22.But, due to lead-in groove 22a shorten length vertically, therefore can suppress the heating of refrigeration agent at front side rotary valve RF as far as possible, thereby improve suction efficiency.
(the second mode of execution)
Next, according to Fig. 5～Fig. 7, the second mode of execution that the present invention specialized is described.In addition, the structure identical with the first mode of execution marked to identical reference character etc. and omit or simplify the explanation of its repetition.
As shown in Fig. 5 and Fig. 7 (a), the first end face 11b is the surface of front casing 13 sides in cylinder block 11, and ，Yu Ge front side, the position suction chamber 17 in the outside that becomes axis hole 11a of the first end face 11b is formed with the first recess 60 accordingly.The first recess 60 forms from the inwall of each front side suction chamber 17 towards radially extending in cylinder block 11.One end of the first recess 60 is at the first end face 11b opening on the axial surface as cylinder block 11, and is connected with the opening of each front side suction chamber 17.The axial length that the other end of the first recess 60 is positioned at front side suction chamber 17, and is not axially connecting cylinder block 11 midway.In addition, the first recess 60 is arranged with towards the second end face 11c from the first end face 11b.
As shown in Fig. 5 and Fig. 7 (b), the second end face 11c be cylinder block 11 axially in the surface of swash plate chamber 25 sides, be formed with accordingly the second recess 61 at the second end face 11c and each front side suction chamber 17.The second recess 61 forms from the inwall of axis hole 11a and radially extends in cylinder block 11.One end of the second recess 61 is at the second end face 11c opening of cylinder block 11, and is connected with the opening of axis hole 11a.The axial length that the other end of the second recess 61 is positioned at axis hole 11a, and is not axially connecting cylinder block 11 midway.In addition, the second recess 61 be arranged with into from the second end face 11c towards the first end face 11b.In addition, the opening of the second end face 11c side (swash plate chamber 25 sides) in the second recess 61 is by thrust-bearing 26 obturations.
And, in cylinder block 11, the first recess 60 is connected and is communicated with the second recess 61, thereby form access 62 for suction chamber.Suction chamber forms with the opening of front side suction chamber 17 sides of an end in the first recess 60 of access 62, and suction chamber forms with the opening of the axis hole 11a side of the other end in the second recess 61 of access 62.And, by this access 62 for suction chamber, front side suction chamber 17 can be communicated with lead-in groove 22a.In addition, at suction chamber, with in access 62, the opening end of swash plate chamber 25 sides is by thrust-bearing 26 obturations, thereby suction chamber is with sealed between access 62 and swash plate chamber 25.The first recess 60 and the second recess 61 form with front side suction chamber 17 and are complementary when by casting, making cylinder block 11.
Fig. 6 is the figure at circumferentially deploying by front side rotary valve RF, by the profile line meaned by solid line, means that the side face of front side rotary valve RF and front side rotary valve RF insert the axis hole 11a of logical supporting.Illustrate lead-in groove 22a in above-mentioned profile line.In addition, double dot dash line by Fig. 6, the front side cylinder bores access 50b that is illustrated in axis hole 11a opening and is communicated with each front side cylinder bores 28, and, suction chamber use access 62(the first recess 60 and the overlapping zone of the second recess 61 that are illustrated in axis hole 11a opening and are communicated with each front side suction chamber 17).
As shown in Figure 6, circumferentially alternately dispose access 50b and access 62 for suction chamber for the front side cylinder bores along axis hole 11a.And, in order to make suction chamber by lead-in groove 22a, with access 62, with the front side cylinder bores, with access 50b, be communicated with, as long as forming along the circumferential part of running shaft 22, extends lead-in groove 22a.
Therefore, according to the second mode of execution, except the identical advantage in (1)～(10) of putting down in writing with the first mode of execution, can also obtain following advantage.
(11) suction chamber becomes in axial longer rectangular with access 62, and therefore at axis hole 11a, suction chamber separates with the degree that can guarantee sealing with access 50b with the front side cylinder bores with access 62 and circumferentially alternately arranging.Therefore, make to be communicated with front side suction chamber 17 in circumferential adjacent front side cylinder bores 28 in order to utilize front side rotary valve RF, and only make to be communicated with and to get final product by lead-in groove 22a with access 62 with suction chamber with access 50b in circumferentially adjacent front side cylinder bores.Therefore, only at front side rotary valve RF, lead-in groove 22a being formed to the shape of extending along the circumferential part of front side rotary valve RF gets final product.Therefore, can be reduced at the shape of the front side rotary valve RF of running shaft 22 formation, thereby can shorten length vertically.Its result, adopt front side rotary valve RF even possess the suction of the compressor 10 of front side suction chamber 17 in cylinder block 11, and build vertically can not maximize yet.
(12) suction chamber, forms in the lump with front side suction chamber 17 with access 62 when cast block 11.Therefore, if, with after cast block 11, by cutting such as drill bits, suction chamber is set and compares by the situation of access 62, save the man-hour of making cylinder block 11.
(13) suction chamber is that the first recess 60 will extended from the first end face 11b is connected and forms with the second recess 61 extended from the second end face 11c with access 62.Thus, and only by the second recess 61, form suction chamber and compare by the situation of access, can suppress the opening area of the second recess 61, thus can be by the opening of more small-sized inaccessible the second recess 61 of thrust-bearing 26.
In addition, above-mentioned mode of execution also can be changed as follows.
In mode of execution, though form access 62 for suction chamber with first recess 60 that will extend from the first end face 11b of cylinder block 11 with the mode that the second recess 61 extended from the second end face 11c is connected, be not limited to this.As shown in Figure 8, as long as the external diameter of thrust-bearing 26 is enough large, second recess 66 that also can only be extended by the second end face 11c from cylinder block 11 forms the suction chamber access.This second recess 66 can directly be communicated with front side suction chamber 17 with lead-in groove 22a.
Suction path as refrigerant gas with respect to front side cylinder bores 28, except utilizing front side rotary valve RF to use the path of access 50b via the front side cylinder bores from suction chamber with access 62, as shown in Figure 9, also can arrange via with the enter the room path of the 19 axle inner gateways 65 that are communicated with of rear casing side draught.In this case, with only from rear casing side draught 19 structures that via axle inner gateway 65, refrigeration agent sucked to front side cylinder bores 28 of entering the room, compare, even side draught enters the room 17 via access 62 for suction chamber in the past, refrigeration agent also can be inhaled into front side cylinder bores 28, therefore can make the diameter miniaturization of axle inner gateway 65.Therefore, running shaft 22, rotary valve RF can be in radially miniaturizations, thereby the build of compressor 10 integral body also can miniaturization.
In mode of execution, though adopted the suction of rotary valve as front side and rear side, rear side also can be made as the suction that is not rotary valve and is based on suction valve.
In mode of execution, at rear side, though the refrigeration agent of rear side suction chamber 18 is concentrated on to the rear casing side draught, enter the room 19, and enter the room 19 via rear side rotary valve RR suction rear side cylinder bores 29 from the rear casing side draught, be not limited to this.At rear side, also each rear side suction chamber 18 can be communicated with by access via lead-in groove individually with axis hole 12a, and, axis hole 12a can be communicated with by importing path individually with rear side cylinder bores 29, thereby make refrigeration agent be inhaled into rear side cylinder bores 29 via lead-in groove, the importing path of access, rear side rotary valve RR from rear side suction chamber 18.
In mode of execution, though suction port 44 is formed to the cylinder block 11 of front side, such as other the position in cylinder block 12 H such as shell such as grade that also suction port 44 can be formed to rear side.
In mode of execution, be supplied to front side suction chamber 17 and rear side suction chamber 18 though will pass through the refrigeration agent of suction port 44 via the suction path 43 that is formed at cylinder block 11,12, also the refrigeration agent that has passed through suction port 44 can be supplied to front side suction chamber 17 and rear side suction chamber 18 via swash plate chamber 25.
In mode of execution, though three front side, place discharge chambers 40 are respectively configured to one in the gap of adjacent front side cylinder bores 28, front side discharge chamber 40 also can be formed at a place or two places in a concentrated manner.In this case, as shown in figure 10, no matter the angle of swing of running shaft 22 is how, all so that the mode that suction chamber is communicated with lead-in groove 22a all the time with access 62 forms the side face ring-type of a week around the front side of running shaft 22 by the part of lead-in groove 22a.
Though three place's rear side discharge chambers 42 are respectively configured to one between adjacent rear side cylinder bores 29, and rear side discharge chamber 42 also can be formed at a place or two places in a concentrated manner.
In mode of execution, though form three rear side suction chambers 18, and rear side suction chamber 18 is respectively configured to one in the gap of adjacent rear side cylinder bores 29, be not limited to this.Also can only the suction space of rear side be made as to the rear casing side draught and enter the room 19, in addition, also rear side suction chamber 18 can be formed in a concentrated manner to a place or two places.
In mode of execution, though it is larger than the volume of other two front side suction chambers 17 that the volume of the front side suction chamber 17 that will be communicated with suction path 43 is made as, also the volume of other two front side suction chambers 17 can be made as larger than the volume of the front side suction chamber 17 be communicated with suction path 43.In situation as constructed as above, from sucking path 43 to the direct supply system cryogen of front side suction chamber 17 with sucking path 43 and being communicated with, for refrigeration agent successfully carries out to 28 supplies of front side cylinder bores, volume also can dwindle.On the other hand, the refrigeration agent that other two front side suction chambers 17 temporarily will be supplied to accommodation chamber 13c is supplied to front side cylinder bores 28, therefore in order successfully to carry out, to front side cylinder bores 28 supply system cryogens, guarantees that large volume is supplied with more refrigeration agent better.
Also three front side suction chambers 17 can be made as to identical volume.
In mode of execution, front side suction chamber 17 and front side discharge chamber 40 form with cylinder block 11 both sides' mode to cross over front casing 13, but also can only be formed at cylinder block 11.
In mode of execution, rear side suction chamber 18 and rear side discharge chamber 42 form with cylinder block 12 both sides' mode to cross over rear casing 14, but also can only be formed at cylinder block 12.
In mode of execution, though oblique tray type compressor is embodied as to the double-headed piston type oblique tray type compressor, also can be connected with swash plate 24, double-head piston 30 is made as to single head pison, thereby oblique tray type compressor is changed to single head pison type oblique tray type compressor.
Symbol description
RF ... front side rotary valve as rotary valve; 10 ... the double-headed piston type oblique tray type compressor; 11,12 ... cylinder block; 11a, 12a ... axis hole; 17 ... the front side suction chamber; 18 ... the rear side suction chamber; 22 ... running shaft; 22a ... lead-in groove; 24 ... swash plate; 25 ... the swash plate chamber; 26,27 ... thrust-bearing; 28 ... front side cylinder bores as cylinder bores; 28b ... front side discharge chamber as discharge chamber; 29 ... rear side cylinder bores as cylinder bores; 29b ... rear side discharge chamber as discharge chamber; 30 ... double-head piston; 32,33 ... outside pipe arrangement; 40 ... front side discharge chamber as discharge chamber; 42 ... rear side discharge chamber as discharge chamber; 43 ... suck path; 44 ... suction port; 50a ... the suction chamber access; 50b ... front side cylinder bores access; 60 ... the first recess; 61,66 ... the second recess; 62 ... the suction chamber access.
Claims (8)
1. an oblique tray type compressor is characterized in that possessing:
Cylinder block, it has axis hole, a plurality of cylinder bores, swash plate chamber and suction chamber, described axis hole extends in the mode that connects described cylinder block, described a plurality of cylinder bores is around described axis hole along circumferential array, and described suction chamber arranges discretely in gap and the described swash plate chamber of adjacent cylinder bores;
Swash plate, it is incorporated in described swash plate chamber;
A plurality of pistons, they are connected with described swash plate and are inserted through respectively described a plurality of cylinder bores;
Running shaft, it is inserted through described axis hole and rotates with described swash plate one; And
Rotary valve, it is arranged at this running shaft in the mode with described running shaft one rotation,
Described cylinder block has access and a plurality of cylinder bores access that described a plurality of cylinder bores is communicated with described axis hole respectively individually for suction chamber that described suction chamber is communicated with described axis hole,
Thereby described rotary valve makes described suction chamber be communicated with successively with access with described a plurality of cylinder bores with access with described running shaft one rotation.
2. oblique tray type compressor according to claim 1, is characterized in that,
Described suction chamber comprises a plurality of suction chambers that lay respectively at the gap of adjacent cylinder bores,
Described suction chamber comprises a plurality of suction chamber access that described a plurality of suction chamber is communicated with described axis hole respectively individually with access.
3. oblique tray type compressor according to claim 2, is characterized in that,
Described cylinder block has a plurality of discharge chambers that lay respectively at the gap of adjacent cylinder bores.
4. oblique tray type compressor according to claim 3, is characterized in that,
Described a plurality of discharge chamber in the radial arrangement of described cylinder block in the outside of described suction chamber.
5. according to the described oblique tray type compressor of any one in claim 1～4, it is characterized in that,
Described cylinder block has the suction port connected for outside pipe arrangement and the suction path that described suction port is communicated with described suction chamber,
Described suction channel setting is for to separate with described swash plate chamber.
6. according to the described oblique tray type compressor of any one in claim 1～5, it is characterized in that,
With access, the recess by the inwall that is formed at described axis hole forms described suction chamber, and this recess has the opening end be communicated with described swash plate chamber,
Configure thrust-bearing between the opening end of described swash plate and described recess,
Described thrust-bearing is by the opening end obturation of described recess.
7. according to the described oblique tray type compressor of any one in claim 1～5, it is characterized in that,
Described suction chamber consists of the first recess and the second recess with access, described the first recess is formed at the inwall of described suction chamber and has the opening end at the axial end face opening of described cylinder block, described the second recess is formed at the inwall of described axis hole and has the opening end be communicated with described swash plate chamber
Configure thrust-bearing between the opening end of described swash plate and described the second recess,
Described thrust-bearing is by the opening end obturation of described the second recess.
8. according to the described oblique tray type compressor of any one in claim 1～7, it is characterized in that,
Described a plurality of cylinder bores is three cylinder bores.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-079843 | 2011-03-31 | ||
| JP2011079843 | 2011-03-31 | ||
| PCT/JP2012/058407 WO2012133669A1 (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103459846A true CN103459846A (en) | 2013-12-18 |
Family
ID=46931371
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012800149814A Pending CN103459846A (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20130343922A1 (en) |
| JP (1) | JP5574041B2 (en) |
| KR (1) | KR101450596B1 (en) |
| CN (1) | CN103459846A (en) |
| BR (1) | BR112013025034A2 (en) |
| WO (1) | WO2012133669A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114585813A (en) * | 2019-10-02 | 2022-06-03 | 株式会社丰田自动织机 | Piston type compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5915576B2 (en) * | 2013-03-27 | 2016-05-11 | 株式会社豊田自動織機 | Piston type swash plate compressor |
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| US3801227A (en) * | 1970-10-17 | 1974-04-02 | Toyoda Automatic Loom Works | Swash-plate type compressor for air conditioning of vehicles |
| US5401144A (en) * | 1992-05-13 | 1995-03-28 | Kabushiki Kaisha Toyoda Jisoshokki Seisakusho | Swash plate type refrigerant compressor |
| JPH08135568A (en) * | 1994-11-04 | 1996-05-28 | Toyota Autom Loom Works Ltd | Reciprocation type compressor |
| JP2004239067A (en) * | 2003-02-03 | 2004-08-26 | Honda Motor Co Ltd | Rotary fluid machinery |
| JP2005163581A (en) * | 2003-12-01 | 2005-06-23 | Honda Motor Co Ltd | Rotating fluid machine |
| US20100003146A1 (en) * | 2008-07-02 | 2010-01-07 | Kabushiki Kaisha Toyota Jidoshokki | Piston type compressor |
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|---|---|---|---|---|
| US3352485A (en) * | 1965-10-22 | 1967-11-14 | Toyoda Automatic Loom Works | Swash plate compressor for use in air conditioning system for vehicles |
| US3750848A (en) * | 1970-10-15 | 1973-08-07 | Toyoda Kk | Apparatus for lubricating a rotary swash plate type compressor |
| JPS5849433Y2 (en) * | 1978-10-16 | 1983-11-11 | 株式会社ボッシュオートモーティブ システム | Rotating swash plate compressor |
| JP2616295B2 (en) * | 1991-09-02 | 1997-06-04 | 株式会社豊田自動織機製作所 | Swash plate compressor for refrigeration equipment |
| US5267839A (en) * | 1991-09-11 | 1993-12-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocatory piston type compressor with a rotary valve |
| JP4946340B2 (en) * | 2005-10-17 | 2012-06-06 | 株式会社豊田自動織機 | Double-head piston compressor |
| JP4702145B2 (en) | 2006-03-31 | 2011-06-15 | 株式会社豊田自動織機 | Swash plate compressor |
| JP5045555B2 (en) * | 2008-05-29 | 2012-10-10 | 株式会社豊田自動織機 | Double-head piston type swash plate compressor |
| KR101001575B1 (en) * | 2008-12-09 | 2010-12-17 | 주식회사 두원전자 | swash plate type compressor with rotary valve |
-
2012
- 2012-03-29 US US14/002,801 patent/US20130343922A1/en not_active Abandoned
- 2012-03-29 JP JP2013507731A patent/JP5574041B2/en not_active Expired - Fee Related
- 2012-03-29 CN CN2012800149814A patent/CN103459846A/en active Pending
- 2012-03-29 KR KR1020137025362A patent/KR101450596B1/en not_active IP Right Cessation
- 2012-03-29 WO PCT/JP2012/058407 patent/WO2012133669A1/en active Application Filing
- 2012-03-29 BR BR112013025034A patent/BR112013025034A2/en not_active IP Right Cessation
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3801227A (en) * | 1970-10-17 | 1974-04-02 | Toyoda Automatic Loom Works | Swash-plate type compressor for air conditioning of vehicles |
| US5401144A (en) * | 1992-05-13 | 1995-03-28 | Kabushiki Kaisha Toyoda Jisoshokki Seisakusho | Swash plate type refrigerant compressor |
| JPH08135568A (en) * | 1994-11-04 | 1996-05-28 | Toyota Autom Loom Works Ltd | Reciprocation type compressor |
| JP2004239067A (en) * | 2003-02-03 | 2004-08-26 | Honda Motor Co Ltd | Rotary fluid machinery |
| JP2005163581A (en) * | 2003-12-01 | 2005-06-23 | Honda Motor Co Ltd | Rotating fluid machine |
| US20100003146A1 (en) * | 2008-07-02 | 2010-01-07 | Kabushiki Kaisha Toyota Jidoshokki | Piston type compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114585813A (en) * | 2019-10-02 | 2022-06-03 | 株式会社丰田自动织机 | Piston type compressor |
| CN114585813B (en) * | 2019-10-02 | 2023-06-06 | 株式会社丰田自动织机 | Piston compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5574041B2 (en) | 2014-08-20 |
| WO2012133669A1 (en) | 2012-10-04 |
| JPWO2012133669A1 (en) | 2014-07-28 |
| BR112013025034A2 (en) | 2016-12-27 |
| KR20130131450A (en) | 2013-12-03 |
| KR101450596B1 (en) | 2014-10-14 |
| US20130343922A1 (en) | 2013-12-26 |
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