CN104074710A - Piston type swash plate compressor - Google Patents
Piston type swash plate compressor Download PDFInfo
- Publication number
- CN104074710A CN104074710A CN201410116904.0A CN201410116904A CN104074710A CN 104074710 A CN104074710 A CN 104074710A CN 201410116904 A CN201410116904 A CN 201410116904A CN 104074710 A CN104074710 A CN 104074710A
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- Prior art keywords
- side discharge
- discharge chamber
- chamber
- cylinder body
- rotor housing
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Classifications
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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
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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
- F04B25/00—Multi-stage pumps
- F04B25/04—Multi-stage pumps 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
- F04B39/0027—Pulsation and noise damping means
- F04B39/0033—Pulsation and noise damping means with encapsulations
- F04B39/0038—Pulsation and noise damping means with encapsulations of inlet or outlet channels
Abstract
A piston type swash plate compressor includes a housing, a cylinder block, a cylinder head, a rotary shaft, a plurality of cylinder bores, a plurality of pistons, a swash plate, a plurality of compression chambers, a plurality of head-side discharge chambers, a plurality of block-side discharge chambers, an outlet and a discharge path. The head-side discharge chambers are provided in the cylinder head. The block-side discharge chambers are provided in the cylinder block. The outlet is formed through the housing. The discharge path is formed in the housing and refrigerant gas is flowed through the discharge path from the compression chamber to the outlet through the head-side discharge chamber to the block-side discharge chamber. After refrigerant gas flowed from the compression chamber is flowed through one head-side discharge chamber which communicates with the compression chamber and one block-side discharge chamber, the refrigerant gas is flowed to another head-side discharge chamber.
Description
Technical field
The present invention relates to a kind of piston type swashplate compressor.
Background technique
In piston type swashplate compressor, refrigerant gas is introduced in pressing chamber and by the to-and-fro motion of piston and the rotary compression of swash plate discharge.In piston type swashplate compressor, caused the generation of vibration and noise by the pulsation of refrigerant gas.A kind of baffler comprising for reducing pulsation has been proposed.For example, Japanese Patent Application No.10-89251 discloses a kind of compressor, wherein, be formed with silencer space in compressor housing, pressing chamber is connected to silencer space and sinuous member is arranged in this silencer space for being defined for the passage that exhausting air is wriggled.
But if silencer space is formed in piston type swashplate compressor to reduce pulsation as in Japanese Patent Application No.10-89251, compressor housing stretches out and the size of piston type swashplate compressor increases.The present invention who considers above problem and propose aims to provide a kind of can reducing and pulses and the less piston type swashplate compressor of size.
Summary of the invention
According to the present invention, piston type swashplate compressor comprises housing, gray iron, running shaft, multiple cylinder thorax, multiple piston, swash plate, multiple pressing chamber, multiple lid side discharge chamber, multiple cylinder body side discharge chamber, outlet and discharge route.Cylinder body is formed in housing.Cylinder cap is formed in housing and is connected to the end of cylinder body.Running shaft is supported in rotatable mode by cylinder body.Multiple cylinder thoraxes are arranged around running shaft.Multiple pistons are correspondingly contained in cylinder thorax.Swash plate rotates integratedly with running shaft and engages with piston.Multiple pressing chambers are limited in cylinder thorax by piston respectively.Multiple lid side discharge chambers are arranged in cylinder cap.Multiple cylinder body side discharge chambers are arranged in cylinder body.Outlet is formed in housing, and the refrigerant gas of compression flows to outside via this outlet.Discharge path is formed in housing, and refrigerant gas flows through from pressing chamber via this discharge path and covers side discharge chamber, flow to cylinder body side discharge chamber and flow to outlet.After the refrigerant gas flowing out from pressing chamber flows through the lid side discharge chamber being communicated with pressing chamber and flows through a cylinder body side discharge chamber, refrigerant gas flows to another lid side discharge chamber.
Other aspects of the present invention and advantage will become obvious from the following description of doing in conjunction with the accompanying drawing that principle of the present invention is shown by way of example.
Brief description of the drawings
With reference to the following description of preferred implementation at present, can understand best the present invention and object and advantage in conjunction with the drawings, in the accompanying drawings:
Fig. 1 is the sectional view intercepting along the line I-I in Fig. 3, there is shown double-headed piston type slant plate type compressor according to the first preferred embodiment of the present invention;
Fig. 2 is the sectional view intercepting along the line II-II in Fig. 3, there is shown the double-headed piston type slant plate type compressor of Fig. 1;
Fig. 3 is the sectional view intercepting along the line III-III in Fig. 1, there is shown protecgulum side discharge chamber and the front suction chamber of the double-headed piston type slant plate type compressor of Fig. 1;
Fig. 4 is the sectional view intercepting along the line IV-IV in Fig. 1, there is shown front-bank rotor housing side discharge chamber and the front suction chamber of the double-headed piston type slant plate type compressor of Fig. 1;
Fig. 5 is the sectional view intercepting along the line V-V in Fig. 1, there is shown protecgulum side discharge chamber and the front bulkhead of the double-headed piston type slant plate type compressor of Fig. 1;
Fig. 6 is the sectional view that shows the protecgulum side discharge chamber of launching, front pressing chamber and the front-bank rotor housing side discharge chamber of the double-headed piston type slant plate type compressor of Fig. 1 in the sense of rotation of running shaft; And
Fig. 7 is the sectional view intercepting along the line VII-VII in Fig. 1, there is shown bonnet side discharge chamber and the rear partition wall of the double-headed piston type slant plate type compressor of Fig. 1.
Embodiment
Below with reference to Fig. 1 to Fig. 7, the piston type swashplate compressor that is embodied as double-headed piston type slant plate type compressor according to the preferred embodiment of the present invention is described.As depicted in figs. 1 and 2, reference character 10 represents that double-headed piston type slant plate type compressor (hereafter is " compressor ") and compressor 10 comprise housing H and be connected to a pair of front-bank rotor housing 11 and rear-bank rotor housing 12 each other.In the housing H of compressor 10, it is upper and be attached to the front end of front-bank rotor housing 11 by front valve board assembly 15 that front end housing 13 is arranged on the front side (left side in Fig. 1) of compressor 10.Front valve board assembly 15 comprises liner G and valve plate 20, and wherein, liner G is for sealing space between front-bank rotor housing 11 and front end housing 13, the part formation of valve plate 20 by after the front expulsion valve 15B that is described.It is upper and be attached to the rear end of rear-bank rotor housing 12 by rear valve board assembly 16 that back cylinder cover 14 is arranged on the rear side (right side in Fig. 1) of compressor 10.Rear valve board assembly 16 comprises liner G and rear valve plate 21, and wherein, liner G is for sealing space between rear-bank rotor housing 12 and back cylinder cover 14, the part formation of rear valve plate 21 by after the rear expulsion valve 16B that is described.Front end housing 13 and back cylinder cover 14 and described a pair of front-bank rotor housing 11 and rear-bank rotor housing 12 between front end housing 13 and back cylinder cover 14 coordinate to form housing H.Front-bank rotor housing 11 and rear-bank rotor housing 12 are as cylinder body of the present invention.Front end housing 13 and back cylinder cover 14 are as cylinder cap of the present invention.Front valve board assembly 15 and rear valve board assembly 16 are as valve board assembly of the present invention.Front expulsion valve 15B and rear expulsion valve 16B are as expulsion valve of the present invention.Front valve plate 20 and rear valve plate 21 are as valve plate of the present invention.
Front-bank rotor housing 11 and rear-bank rotor housing 12 comprise respectively front-axle hole 11A and rear axis hole 12A, and running shaft 22 inserts through front-axle hole 11A and rear axis hole 12A rotatably to be supported by the interior perimeter surface that forms sealing peripheral surface of front-axle hole 11A and rear axis hole 12A.Front valve board assembly 15 and rear valve board assembly 16 comprise respectively the front patchhole 15D and the rear patchhole 16D that locate in the central formation, and running shaft 22 inserts through front patchhole 15D and rear patchhole 16D.Space between the outer surface of the front end that extends front valve board assembly 15 and the interior perimeter surface of front end housing 13 of the shaft seal 23 sealing rotary rotating shaft airtightly 22 of lip seal type.Shaft seal 23 is arranged in accommodating chamber 13C, and this accommodating chamber 13C is formed between the interior perimeter surface of front-bank rotor housing lid 13 and the outer surface of running shaft 22.Front-axle hole 11A and rear axis hole 12A are as axis hole of the present invention.Front patchhole 15D and rear patchhole 16D are as patchhole of the present invention.
The swash plate 24 rotating integratedly with running shaft 22 is firmly-fixed to running shaft 22.Swash plate 24 is arranged in crankshaft room 25, and this crankshaft room 25 is formed between front-bank rotor housing 11 and rear-bank rotor housing 12.Forward thrust bearing 26 is between the rear end surface of front-bank rotor housing 11 and the annular base 24A of swash plate 24.Back pressure bearing 27 is between the front end surface of rear-bank rotor housing 12 and the base portion 24A of swash plate 24.Forward thrust bearing 26 and back pressure bearing 27 keep swash plate 24 and the moving of the axis L along running shaft 22 of regulate/restriction swash plate 24.Forward thrust bearing 26 and back pressure bearing 27 are as thrust-bearing of the present invention.
As shown in Figure 4, in front-bank rotor housing 11, arrange/be furnished with three front cylinder thoraxes 28 around running shaft 22.As shown in Figure 1, in rear-bank rotor housing 12, be provided with three around running shaft 22 after cylinder thorax 29.The axis L (along the longitudinal direction of compressor 10) that paired front cylinder thorax 28 and rear cylinder thorax 29 are formed as along running shaft 22 is extended.In front cylinder thorax 28 and rear cylinder thorax 29, receive and have double-head piston 30 respectively.Front cylinder thorax 28 is by front valve board assembly 15 and double-head piston 30 seals and rear cylinder thorax 29 is sealed by rear valve board assembly 16 and double-head piston 30.Front cylinder thorax 28 and rear cylinder thorax 29 are as cylinder thorax of the present invention.
Rotatablely moving by keeping a pair of sliding shoes 31 of swash plate 24 to be passed to double-head piston 30 from its opposite side of the swash plate 24 rotating integratedly with running shaft 22.Double-head piston 30 to-and-fro motion in front cylinder thorax 28 and rear cylinder thorax 29.Front pressing chamber 28A is limited in cylinder thorax 28 by double-head piston 30 and front valve board assembly 15, and rear pressing chamber 29A is limited in rear cylinder thorax 29 by double-head piston 30 and rear valve board assembly 16.Front pressing chamber 28A and rear pressing chamber 29A are as pressing chamber of the present invention.
As shown in Figure 1 and Figure 4, be formed with suction chamber 18 after three front suction chambers 17 and three around running shaft 22, and it extends through front valve board assembly 15 and rear valve board assembly 16 in front end housing 13 and front-bank rotor housing 11 and back cylinder cover 14 and rear-bank rotor housing 12.Each front suction chamber 17 all between any two adjacent front cylinder thoraxes 28 and each rear suction chamber 18 all between any two adjacent rear cylinder thoraxes 29.Front suction chamber 17 and rear suction chamber 18 are separately positioned on the outer circumferential side of front-axle hole 11A and rear axis hole 12A with the interval equating.Front suction chamber 17 has than length and volume on the axial direction of the length of other front suction chambers 17 and the larger running shaft 22 of volume, and after one, suction chamber 18 has than length and volume on the axial direction of the length of suction chambers 18 after other and the larger running shaft 22 of volume.Front suction chamber 17 and rear suction chamber 18 are as suction chamber of the present invention.
As shown in figures 1 and 3, in front end housing 13, the each suction chamber in three front suction chambers 17 is all communicated with accommodating chamber 13C, and three front suction chambers 17 communicate with each other by accommodating chamber 13C.Therefore, three front suction chambers 17 and accommodating chamber 13C form a space.
As shown in Fig. 1, Fig. 3 and Fig. 7, three the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C are positioned between front end housing 13 and front valve board assembly 15 around running shaft 22, and three the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C are positioned between back cylinder cover 14 and rear valve board assembly 16 around running shaft 22.In the past the refrigerant gas that pressing chamber 28A and rear pressing chamber 29A flow out is disposed to respectively the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C.Front space 28B is formed in front end housing 13 and is separated into the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C around running shaft 22.Rear space 29B is formed in back cylinder cover 14 and is separated into the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C around running shaft 22.The first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C by front valve board assembly 15 with rear valve board assembly 16 and towards the size and cylinder thorax 28 and rear cylinder thorax 29 before front pressing chamber 28A and rear pressing chamber 29A(of front pressing chamber 28A and the opening of the position of rear pressing chamber 29A) circular cross-section identical.The first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C are as lid side discharge chamber of the present invention.Front space 28B and rear space 29B are as space of the present invention.
In front-bank rotor housing 11, be formed with three front-bank rotor housing side discharge chambers 40, and in rear-bank rotor housing 12, be formed with three rear-bank rotor housing side discharge chambers 42.Front pressing chamber 28A, the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and front-bank rotor housing side discharge chamber 40 communicate with each other, and rear pressing chamber 29A, the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C and rear-bank rotor housing side discharge chamber 42 communicate with each other.Three front-bank rotor housing side discharge chambers 40 around running shaft 22 locate and each front-bank rotor housing side discharge chamber 40 all between any two adjacent front cylinder thoraxes 28.Three rear-bank rotor housing side discharge chambers 42 around running shaft 22 locate and each rear-bank rotor housing side discharge chamber 42 all between any two adjacent rear cylinder thoraxes 29.Front-bank rotor housing side discharge chamber 40 is formed on the outer circumferential side of the radial direction along front-bank rotor housing 11 of front suction chamber 17, and be formed on the outer circumferential side of the radial direction along rear-bank rotor housing 12 of rear suction chamber 18/side of rear-bank rotor housing side discharge chamber 42.Front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42 are as cylinder body side discharge chamber of the present invention.
In front valve board assembly 15, be formed with the front exhaust port 15A being positioned at towards the position of the front cylinder thorax 28 of correspondence, and in rear valve board assembly 16, be formed with the rear exhaust port 16A being positioned at towards the position of the rear cylinder thorax 29 of correspondence.In front valve plate 20, be formed with the front expulsion valve 15B being positioned at towards the position of the front exhaust port 15A of correspondence, and in rear valve plate 21, be formed with the rear expulsion valve 16B being positioned at towards the position of the rear exhaust port 16A of correspondence.In front valve board assembly 15, be formed with front holder 15C correspondingly to regulate the opening degree of front expulsion valve 15B, and be formed with rear holder 16C correspondingly to regulate the opening degree of rear expulsion valve 16B in rear valve board assembly 16.Front exhaust port 15A is communicated with the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C respectively, and rear exhaust port 16A is communicated with the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C respectively.In the past the refrigerant gas that pressing chamber 28A flows out flows to the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C, and the refrigerant gas flowing out from rear pressing chamber 29A flows to the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C.Front exhaust port 15A and rear exhaust port 16A are as exhaust port of the present invention.Front holder 15C and rear holder 16C are as holder of the present invention.
As shown in Figure 1, in front-bank rotor housing 11 and rear-bank rotor housing 12, be formed with suction passage 43.The opening of the front end of suction passage 43 is communicated with the front suction chamber 17 in the middle of three front suction chambers 17 with maximum volume.The opening of the rear end of suction passage 43 is communicated with the rear suction chamber 18 in the middle of suction chamber 18 after three with maximum volume.In front-bank rotor housing 11, be formed with import 44.The other end lead to/the opening of one end of import 44 by front-bank rotor housing 11/ opening and import 44 through front-bank rotor housing 11 is to suction passage 43.The external refrigeration loop that is arranged on compressor 10 outsides is connected to the opening of one end of import 44.
Suction passage 43 is formed as being communicated with front suction chamber 17 and rear suction chamber 18, and each one in this front suction chamber 17 and rear suction chamber 18 has maximum volume in the middle of front suction chamber 17 and rear suction chamber 18 on front side and rear side.Therefore, suction passage 43 is in axial direction arranged between the front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42 on the outer circumferential side of front suction chamber 17 and rear suction chamber 18.
As shown in Figure 2, in front-bank rotor housing 11 and rear-bank rotor housing 12, be formed with discharge route 45.The opening of the front end of discharge route 45 is communicated with a front-bank rotor housing side discharge chamber in three front-bank rotor housing side discharge chambers 40 and the opening of the rear end of discharge route 45 is communicated with a rear-bank rotor housing side discharge chamber in three rear-bank rotor housing side discharge chambers 42.In addition, be formed with outlet 46 through front-bank rotor housing 11 or housing H.Outlet one end of 46 is by front-bank rotor housing 11(housing H) and export 46 the other end and lead to discharge route 45.The external refrigeration loop that is arranged on compressor 10 outsides is connected to outlet 46.As shown in Figure 3, discharge route 45 is formed in front-bank rotor housing 11 and rear-bank rotor housing 12, is positioned at from suction passage 43 along front-bank rotor housing 11 and the position of the sense of rotation of rear-bank rotor housing 12 skew.Front pressing chamber 28A is communicated with discharge route 45 by the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and front-bank rotor housing side discharge chamber 40.Rear pressing chamber 29A is communicated with discharge route 45 by bonnet side discharge chamber 35A to 35C and rear-bank rotor housing side discharge chamber 42.Therefore, in housing H, be formed with in the past pressing chamber 28A and rear pressing chamber 29A and extend to by the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C, front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42 and discharge route 45 discharge path of outlet 46.
At compressor 10, in the case of using for the refrigerating circuit of vehicle air conditioning, external refrigeration loop is connected the outlet of compressor 10 46 with import 44.External refrigeration loop comprises being arranged in the following order condenser, expansion valve and the vaporizer external refrigeration loop from the outlet 46 of compressor 10.
Below by the suction structure of describing in compressor 10.As shown in Figure 1 and Figure 4, in front-bank rotor housing 11, be formed with communicating passage 50A for correspondingly front suction chamber 17 being communicated with front-axle hole 11A.The other end that front suction chamber 17 and communicating passage 50A are led in one end of communicating passage 50A leads to front-axle hole 11A at its sealing peripheral surface place.Communicating passage 50A is formed in front-bank rotor housing 11 slightly to extend in low dip in the radial direction along front-bank rotor housing 11.
In front-bank rotor housing 11, be formed with introduction passage 50B for front-axle hole 11A is correspondingly communicated with front cylinder thorax 28.Front-axle hole 11A is led at its sealing peripheral surface place in one end of introduction passage 50B, and the other end of introduction passage 50B leads to front cylinder thorax 28.Communicating passage 50A and introduction passage 50B alternately arrange along the sense of rotation of running shaft 22.Communicating passage 50A and introduction passage 50B lead to front-axle hole 11A at the same position place of the axial direction along front-axle hole 11A.
In peripheral surface on the front side of running shaft 22, be formed with forward recess 22A.Forward recess 22A is recessed in the peripheral surface in front end housing 13 sides of running shaft 22.Forward recess 22A leads to/is opened on front-axle hole 11A and be communicated with communicating passage 50A and introduction passage 50B at sealing peripheral surface place.According to the rotation of running shaft 22, the position of forward recess 22A is changed mechanically to switch the communication path between communicating passage 50A and introduction passage 50B and forward recess 22A.
Therefore, the part that the sealed peripheral surface of running shaft 22 is surrounded is front rotary valve RF, and this front rotary valve RF and running shaft 22 form.Forward recess 22A be configured to by a communicating passage 50A be positioned in the sense of rotation of running shaft 22 on an introduction passage 50B adjacent with communicating passage 50A be communicated with.According to the rotation of running shaft 22, communicating passage 50A is communicated with introduction passage 50B by forward recess 22A, and refrigerant gas the past suction chamber 17 is flow in the front cylinder thorax 28 adjacent with front suction chamber 17.
Below by the suction structure on the rear side of description compressor 10.As depicted in figs. 1 and 2, in rear-bank rotor housing 12, be formed with introduction passage 51 for rear cylinder thorax 29 is correspondingly communicated with rear axis hole 12A.Rear cylinder thorax 29 is correspondingly led in one end of introduction passage 51, and the other end of introduction passage 51 axis hole 12A after sealing peripheral surface place is led to.In the peripheral surface of the rear end of running shaft 22, be formed with rear service duct 22B.The cylindrical shape suction chamber 19 forming in back cylinder cover 14 is led in one end of rear service duct 22B, and the other end of rear service duct 22B is communicated with the other end of introduction passage 51.According to the rotation of running shaft 22, the position of rear service duct 22B is changed mechanically to switch the communication path between introduction passage 51 and rear service duct 22B.Therefore the part that, the sealed peripheral surface of running shaft 22 is surrounded is the rear rotary valve RR forming with running shaft 22.Cylindrical shape suction chamber 19 is as suction chamber of the present invention.
Below by the muffler structure of describing in compressor 10.As shown in Fig. 2, Fig. 3 and Fig. 5, front space 28B is recessed on front end housing 13 with circlewise around running shaft 22.In front end housing 13, be provided with the first front bulkhead 32A to the three front bulkhead 32C for front space 28B being divided/is separated into the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C.The first front bulkhead 32A to the three front bulkhead 32C extend towards front-bank rotor housing side discharge chamber 40 from the bottom surface of front end housing 13.The first front bulkhead 32A is arranged on the position adjacent with front-bank rotor housing side discharge chamber 40 along the sense of rotation of running shaft 22, and wherein, front-bank rotor housing side discharge chamber 40 is communicated with discharge route 45.
The first front bulkhead 32A and the second front bulkhead 32B are arranged to adjacent one another are so that a front cylinder thorax 28 is mediate along the sense of rotation of running shaft 22.Front space 28B comprises the first protecgulum side discharge chamber 33A being formed by the first front bulkhead 32A and the second front bulkhead 32B.The first protecgulum side discharge chamber 33A is by a front exhaust port 15A and pressing chamber 28A before a front cylinder thorax 28() be communicated with.
The second front bulkhead 32B and the 3rd front bulkhead 32C are arranged to adjacent one another are so that another front cylinder thorax 28 is mediate along the sense of rotation of running shaft 22.Front space 28B comprises the second protecgulum side discharge chamber 33B being formed by the second front bulkhead 32B and the 3rd front bulkhead 32C.The second protecgulum side discharge chamber 33B is by a front exhaust port 15A and pressing chamber 28A before a front cylinder thorax 28() be communicated with, wherein, this front cylinder thorax 28 is different from the front cylinder thorax 28 being communicated with the first protecgulum side discharge chamber 33A.Front space 28B comprises the 3rd protecgulum side discharge chamber 33C being formed by the first front bulkhead 32A and the 3rd front bulkhead 32C.The 3rd protecgulum side discharge chamber 33C is by a front exhaust port 15A and the front pressing chamber 28A of front cylinder thorax 28(of residue) be communicated with.The 3rd protecgulum side discharge chamber 33C is communicated with discharge route 45 by front-bank rotor housing side discharge chamber 40.
As shown in Figure 2 and Figure 7, rear space 29B is recessed on back cylinder cover 14 with circlewise around running shaft 22.In back cylinder cover 14, be provided with the first rear partition wall 34A to the three rear partition wall 34C for rear space 29B being divided into three spaces.The first rear partition wall 34A to the three rear partition wall 34C extend towards rear-bank rotor housing side discharge chamber 42 from the bottom surface of back cylinder cover 14.The first rear partition wall 34A is arranged on the position adjacent with rear-bank rotor housing side discharge chamber 42 along the sense of rotation of running shaft 22, and wherein, rear-bank rotor housing side discharge chamber 42 is communicated with discharge route 45.
The first rear partition wall 34A and the second rear partition wall 34B along the sense of rotation of running shaft 22 be arranged to adjacent one another are so that after one cylinder thorax 29 mediate.Rear space 29B comprises the first bonnet side discharge chamber 35A being formed by the first rear partition wall 34A and the second rear partition wall 34B.Exhaust port 16A and pressing chamber 29A after cylinder thorax 29(after after the first bonnet side discharge chamber 35A passes through one) be communicated with.
The second rear partition wall 34B and the 3rd rear partition wall 34C are arranged to adjacent one another are so that another rear cylinder thorax 29 is mediate along the sense of rotation of running shaft 22.Rear space 29B comprises the second bonnet side discharge chamber 35B being formed by the second rear partition wall 34B and the 3rd rear partition wall 34C.The second bonnet side discharge chamber 35B is by exhaust port 16A and pressing chamber 29A after cylinder thorax 29(after after one) is communicated with, wherein, cylinder thorax 29 is different from the rear cylinder thorax 29 of the first bonnet side discharge chamber 35A connection together after this.Rear space 29B also comprises the 3rd bonnet side discharge chamber 35C being formed by the first rear partition wall 34A and the 3rd rear partition wall 34C.The 3rd bonnet side discharge chamber 35C by exhaust port 16A after with remain one after pressing chamber 29A after cylinder thorax 29() be communicated with.The 3rd bonnet side discharge chamber 35C is communicated with discharge route 45 by rear-bank rotor housing side discharge chamber 42.
As shown in Figure 3 and Figure 7, in the liner G of front valve board assembly 15, be formed with two couples of the first front throttle orifice 15F correspondingly to make the second front bulkhead 32B and the 3rd front bulkhead 32C mediate.In the liner G of rear valve board assembly 16, be formed with two couples of the first rear throttle orifice 16F correspondingly to make the second rear partition wall 34B and the 3rd rear partition wall 34C mediate.In front valve plate 20, be formed with two couples of the second front throttle orifice 20A for being communicated with the first front throttle orifice 15F respectively.In rear valve plate 21, be formed with two couples of the second rear throttle orifice 21A for being communicated with the first rear throttle orifice 16F respectively.Intervenient the first paired front throttle orifice 15F of the second front bulkhead 32B and the second paired front throttle orifice 20A are communicated with a front-bank rotor housing side discharge chamber 40.Intervenient the first paired rear throttle orifice 16F of the second rear partition wall 34B and the second paired rear throttle orifice 21A are communicated with a rear-bank rotor housing side discharge chamber 42.Intervenient the first paired front throttle orifice 15F of the 3rd front bulkhead 32C and the second paired front throttle orifice 20A are communicated with other front-bank rotor housing side discharge chamber 40.Intervenient the first paired rear throttle orifice 16F of the 3rd rear partition wall 34C and the second paired rear throttle orifice 21A are communicated with other rear-bank rotor housing side discharge chamber 42.The first protecgulum side discharge chamber 33A and the second protecgulum side discharge chamber 33B are communicated with making intervenient the first paired front throttle orifice 15F of the second front bulkhead 32B and the second paired front throttle orifice 20A by a front-bank rotor housing side discharge chamber 40.The first bonnet side discharge chamber 35A and the second bonnet side discharge chamber 35B are communicated with making intervenient the first paired rear throttle orifice 16F of the second rear partition wall 34B and the second paired rear throttle orifice 21A by a rear-bank rotor housing side discharge chamber 42.The second protecgulum side discharge chamber 33B and the 3rd protecgulum side discharge chamber 33C are communicated with making intervenient the first paired front throttle orifice 15F of the 3rd front bulkhead 32C and the second paired front throttle orifice 20A by other front-bank rotor housing side discharge chamber 40.The second bonnet side discharge chamber 35B and the 3rd bonnet side discharge chamber 35C are communicated with making intervenient the first paired rear throttle orifice 16F of the 3rd rear partition wall 34C and the second paired rear throttle orifice 21A by other rear-bank rotor housing side discharge chamber 42.The first protecgulum side discharge chamber 33A and the 3rd protecgulum side discharge chamber 33C are separated and do not communicate with each other by the first front bulkhead 32A.The first bonnet side discharge chamber 35A and the 3rd bonnet side discharge chamber 35C are separated and do not communicate with each other by the first rear partition wall 34A.As represented by arrow Y in Fig. 3, in front space 28B, refrigerant gas flows to the second protecgulum side discharge chamber 33B and then flows to the 3rd protecgulum side discharge chamber 33C from the first protecgulum side discharge chamber 33A along the sense of rotation of running shaft 22.As represented by arrow Y in Fig. 7, in rear space 29B, refrigerant gas flows to the second bonnet side discharge chamber 35B and then flows to the 3rd bonnet side discharge chamber 35C from the first bonnet side discharge chamber 35A along the sense of rotation of running shaft 22.The first front throttle orifice 15F and the first rear throttle orifice 16F are as first segment discharge orifice of the present invention.The second front throttle orifice 20A and the second rear throttle orifice 21A are as second section discharge orifice of the present invention.
To the as above operation of the compressor 10 of structure be described below.Refrigerant gas flow in suction passage 43 via import 44 and is supplied in front suction chamber 17 and rear suction chamber 18.When current cylinder thorax 28 is converted to suction stroke, a communicating passage 50A communicates with each other by the forward recess 22A of front rotary valve RF with the introduction passage 50B adjacent with communicating passage 50A.Then, refrigerant gas in the past suction chamber 17 flow in front cylinder thorax 28 via front rotary valve RF.
According to the rotation of running shaft 22, forward recess 22A separates with communicating passage 50A, and the connection of communicating passage 50A and introduction passage 50B is blocked, and front cylinder thorax 28 is closed.Therefore, front cylinder thorax 28 is converted to compression stroke and discharge stroke.
With reference to Fig. 6, on the front side of compressor 10, the refrigerant gas that is discharged into the first protecgulum side discharge chamber 33A is passed in the second front throttle orifice 20A and a first front throttle orifice 15F of the second front bulkhead 32B mono-side formation and flow in front-bank rotor housing side discharge chamber 40 along the axial direction of running shaft 22.Then, refrigerant gas passes other the first front throttle orifice 15F with other the second front throttle orifice 20A and flows to the second protecgulum side discharge chamber 33B different from the first protecgulum side discharge chamber 33A along the axial direction of running shaft 22.
The refrigerant gas of discharging from pressing chamber 28A towards the second protecgulum side discharge chamber 33B is passed in the 3rd front bulkhead 32C mono-side formation a pair of the second front throttle orifice 20A along the axial direction of running shaft 22 flow into front-bank rotor housing side discharge chamber 40 with the first front throttle orifice 15F and together with the refrigerant gas flowing out from the first protecgulum side discharge chamber 33A.Then, the axial direction of refrigerant gas from front-bank rotor housing side discharge chamber 40 along running shaft 22 through throttle orifice 15F other first with other the second front throttle orifice 20A and flow to the three protecgulum side discharge chamber 33C different from the second protecgulum side discharge chamber 33B.
The refrigerant gas that is discharged to the 3rd protecgulum side discharge chamber 33C from pressing chamber 28A towards the 3rd protecgulum side discharge chamber 33C flow in front-bank rotor housing side discharge chamber 40 and then flows out to external refrigeration loop via discharge route 45 and outlet 46 together with the refrigerant gas flowing out from the second protecgulum side discharge chamber 33B.
On the rear side of compressor 10, be supplied at refrigerant gas under the state of cylindrical shape suction chamber 19, in the time that rear cylinder thorax 29 is converted to suction stroke, the rear service duct 22B being communicated with cylindrical shape suction chamber 19 in rear rotary valve RR is communicated with an introduction passage 51.Then, refrigerant gas from cylindrical shape suction chamber 19 via rotary valve RR be supplied to introduction passage 51 and flow in the rear cylinder thorax 29 being communicated with introduction passage 51.
According to the rotation of running shaft 22, rear service duct 22B separates with introduction passage 51, and the connection between introduction passage 51 and cylindrical shape suction chamber 19 is blocked, and rear cylinder thorax 29 is closed.Therefore, rear cylinder thorax 29 is converted to compression stroke and discharge stroke.
With reference to Fig. 7, on the rear side of compressor 10, the refrigerant gas that is discharged into the first bonnet side discharge chamber 35A is passed in a second rear throttle orifice 21A that the second rear partition wall 34B mono-side forms and a first rear throttle orifice 16F and flow in rear-bank rotor housing side discharge chamber 42 along the axial direction of running shaft 22.Then, the refrigerant gas in rear-bank rotor housing side discharge chamber 42 passes other the first rear throttle orifice 16F with other the second rear throttle orifice 21A and flow in the second bonnet side discharge chamber 35B different from the first bonnet side discharge chamber 35A along the axial direction of running shaft 22.
The second rear throttle orifice 21A that the refrigerant gas of discharging from pressing chamber 29A towards the second bonnet side discharge chamber 35B is passed in the 3rd rear partition wall 34C mono-side formation along the axial direction of running shaft 22 flow into rear-bank rotor housing side discharge chamber 42 with a first rear throttle orifice 16F and together with the refrigerant gas flowing out from the first bonnet side discharge chamber 35A.Then, the refrigerant gas in rear-bank rotor housing side discharge chamber 42 is along the axial direction of running shaft 22 through in addition/another first rear throttle orifice 16F and in addition/another second rear throttle orifice 21A and flow in the 3rd bonnet side discharge chamber 35C different from the second bonnet side discharge chamber 35B.The refrigerant gas that is discharged into the 3rd bonnet side discharge chamber 35C flow in rear-bank rotor housing side discharge chamber 42, flow through discharge route 45 and together with the refrigerant gas flowing out from the second bonnet side discharge chamber 35B from exporting 46 discharges.
Therefore, on the front side and rear side of compressor 10, the refrigerant gas of pressing chamber 28A and rear pressing chamber 29A discharge can be by utilizing the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C and front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42 to come back and forth in the past.Therefore, make refrigerant gas wriggle until the refrigerant gas discharging from exporting 46 discharges.Because refrigerant gas has viscosity, therefore reduce energy by moving refrigerant gas along the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first internal surface of bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C and the internal surface of front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42.
According to the preferred embodiment of the present invention, obtain following advantageous effects.
(1) on the front side of compressor 10, front-bank rotor housing side discharge chamber 40 can be communicated with from two protecgulum side discharge chambers different in protecgulum side discharge chamber 33A to 33C, and on the rear side of compressor 10, rear-bank rotor housing side discharge chamber 42 can be communicated with from two bonnet side discharge chambers different in the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C.Therefore, refrigerant gas can be in discharge path back and forth, and the refrigerant gas of discharge flows to outlet 46 via this discharge path.Therefore, can make refrigerant gas wriggle.Therefore, the refrigerant gas of discharge flows to outlet 46 distance and can increase to reduce pulsation.Therefore, in order to reduce pulsation, can be without being set up from the baffler chamber that housing H is outstanding.In addition, pulsation can reduce in the situation that baffler chamber is not set in limited volume.
(2) in front-bank rotor housing 11, be formed with outlet 46.Therefore, in the past the refrigerant gas that pressing chamber 28A and rear pressing chamber 29A flow out is discharged along the direction of leaving outlet 46, then refrigerant gas and protecgulum side discharge chamber 33A to 33C and bonnet side discharge chamber 35A to 35C collide, flow in front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42, and flow out to external refrigeration loop via outlet 46.Therefore, compressed refrigerant gas can be back and forth at least one times until refrigerant gas arrives outlet 46.
(3), in front end housing 13 and back cylinder cover 14, front space 28B and rear space 29B form circlewise around running shaft 22 respectively.Therefore,, when refrigerant gas is mobile along the sense of rotation of running shaft 22, the refrigerant gas flowing in front space 28B and rear space 29B is in axial direction wriggled and arrives outlet 46.Therefore, the refrigerant gas of discharge flows to outlet 46 distance and can be increased to reduce pulsation.
(4), in front end housing 13 and back cylinder cover 14, front space 28B and rear space 29B form circlewise around running shaft 22 respectively.Therefore, front space 28B and rear space 29B can easily be separated into the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C by the first front bulkhead 32A to the three front bulkhead 32C and the first rear partition wall 34A to the three rear partition wall 34C.In addition, front space 28B and rear space 29B form around running shaft 22 by utilizing widely front end housing 13 and back cylinder cover 14.Because annular front space 28B and annular rear space 29B are separated by the first front bulkhead 32A to the three front bulkhead 32C and the first rear partition wall 34A to the three rear partition wall 34C, the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C can increase effectively to reduce pulsation as much as possible.
(5) be provided with multiple front-bank rotor housing side discharge chambers 40 and rear-bank rotor housing side discharge chamber 42 around running shaft 22.Therefore, can make refrigerant gas flow into multiple front-bank rotor housing side discharge chambers 40 and rear-bank rotor housing side discharge chamber 42 and by it and back and forth from the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C.Therefore, can guarantee that the gas flow of discharging is to exporting 46 long distance to reduce pulsation.
(6) outlet 46 is communicated with a rear-bank rotor housing side discharge chamber in a front-bank rotor housing side discharge chamber and three rear-bank rotor housing side discharge chambers 42 in three front-bank rotor housing side discharge chambers 40.Therefore the refrigerant gas, flowing into front-bank rotor housing side discharge chamber 40 from the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C can prevent from directly flowing out via outlet 46 from front-bank rotor housing side discharge chamber 40.Similarly, the refrigerant gas flowing into rear-bank rotor housing side discharge chamber 42 from the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C can prevent from directly flowing out via outlet 46 from rear-bank rotor housing side discharge chamber 42.Therefore, can guarantee that the refrigerant gas of discharging flows to outlet 46 distance and reduces pulsation.
(7) front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42 are arranged in the gap between rear cylinder thorax 29 between front cylinder thorax 28 adjacent one another are and adjacent one another are one by one along the sense of rotation of running shaft 22.Therefore, the gap of front cylinder thorax 28 adjacent one another are and rear cylinder thorax 29 is effectively for front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42.The increase of the size on the axial direction of compressor 10 can be suppressed.
(8) first front throttle orifice 15F and the first rear throttle orifice 16F are arranged in the liner of front valve board assembly 15 and rear valve board assembly 16.The second front throttle orifice 20A and the second rear throttle orifice 21A are arranged in front valve plate 20 and rear valve plate 21.The first front throttle orifice 15F and the first rear throttle orifice 16F and the second front throttle orifice 20A and the second rear throttle orifice 21A make the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C be communicated with rear-bank rotor housing side discharge chamber 42 with front-bank rotor housing side discharge chamber 40 and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C.Therefore, in the time that refrigerant gas flows between the first protecgulum side discharge chamber 33A to the three protecgulum side discharge chamber 33C and front-bank rotor housing side discharge chamber 40 and the first bonnet side discharge chamber 35A to the three bonnet side discharge chamber 35C and rear-bank rotor housing side discharge chamber 42, can reduce by the pulsation of the first front throttle orifice 15F and the first rear throttle orifice 16F and the second front throttle orifice 20A and the second rear throttle orifice 21A generation.
Above preferred implementation may be modified as following illustrative various substituting mode of executions.The diameter of the first front throttle orifice 15F and the first rear throttle orifice 16F and the second front throttle orifice 20A and the second rear throttle orifice 21A can be changed.
Can in the miscellaneous part except front valve board assembly 15 and rear valve board assembly 16, form front exhaust port 15A and rear exhaust port 16A.
Only liner G is separately positioned between front-bank rotor housing 11 and front end housing 13 and rear-bank rotor housing 12 and back cylinder cover 14, and front exhaust port 15A and rear exhaust port 16A and the first front throttle orifice 15F and the first rear throttle orifice 16F can be separately positioned in liner G.
Front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42 nonessential setting one by one in the gap of front cylinder thorax 28 adjacent one another are and rear cylinder thorax 29.In some gaps, front-bank rotor housing side discharge chamber 40 and rear-bank rotor housing side discharge chamber 42 can be set.
Four or more next door can be arranged in each one in front end housing 13 and back cylinder cover 14, and four or more front-bank rotor housing side discharge chamber 40 and four or more rear-bank rotor housing side discharge chamber 42 can be set to increase the reciprocal time of refrigerant gas.On the other hand, two next doors can be arranged in each one in front end housing 13 and back cylinder cover 14, and two or more front-bank rotor housing side discharge chambers 40 and two or more rear-bank rotor housing side discharge chambers 42 can be set to reduce the reciprocal time of refrigerant gas.
According to preferred implementation, outlet 46 openings are through front-bank rotor housing 11.Alternatively, outlet can be formed as opening through rear-bank rotor housing 12 or front end housing 13 and back cylinder cover 14.
According to preferred implementation, rotary valve is suitable for sucking on the front side of compressor 10 and rear side.Alternatively, substitute rotary valve, suction valve can be suitable for sucking on front side and rear side.
According to preferred implementation, on the rear side of compressor 10, the refrigerant gas in front suction chamber 18 accumulate in cylindrical shape suction chamber 19 and from cylindrical shape suction chamber 19 via rotary valve RR flow in rear cylinder thorax 29.Alternatively, on the rear side of compressor 10, the same with on front side, rear suction chamber 18 and rear axis hole 12A can and introduce groove by communicating passage and be communicated with, and rear axis hole 12A and rear cylinder thorax 29 can be communicated with by introduction passage respectively dividually.Therefore, refrigerant gas can flow in rear cylinder thorax 29 via introducing groove and the introduction passage of communicating passage, rear rotary valve RR from rear suction chamber 18.
According to preferred implementation, be supplied to front pressing chamber 28A and rear pressing chamber 29A through the refrigerant gas of import 44 via the lip-deep forward recess 22A and the rear service duct 22B that are formed on running shaft 22.Alternatively, running shaft can be used as quill shaft and is formed as comprising therein inner passage.Therefore,, after the refrigerant gas that flows through import 44 can guide to the inside of front end housing 13 or back cylinder cover 14, refrigerant gas is supplied to front pressing chamber 28A and rear pressing chamber 29A via inner passage.
According to preferred implementation, the refrigerant gas that flows through import 44 is supplied to front suction chamber 17 and rear suction chamber 18 via the suction passage 43 being formed in front-bank rotor housing 11 and rear-bank rotor housing 12.Alternatively, the refrigerant gas that flows through import 44 can be supplied to front suction chamber 17 and rear suction chamber 18 via crankshaft room 25.
According to preferred implementation, after the front suction chamber 17 being communicated with suction passage 43 and one, the volume settings of suction chamber 18 is larger than the volume of suction chamber 18 after other two front suction chambers 17 and other two.Alternatively, after other two front suction chambers 17 and other two, the volume of suction chamber 18 can be set as larger than the volume of the front suction chamber 17 being communicated with suction passage 43 and rear suction chamber 18.
Three front suction chambers 17 can have identical volume, and after three, suction chamber 18 also can have identical volume.
A front-bank rotor housing side discharge chamber 40 can be only set, and each front space 28B can be separated into two protecgulum side discharge chambers.A rear-bank rotor housing side discharge chamber 42 can be only set, and each rear space 29B can be separated into two bonnet side discharge chambers.
The number of front cylinder thorax 28 and rear cylinder thorax 29 can be changed.
According to preferred implementation, compressor 10 is the double-headed piston type slant plate type compressor that comprises double-head piston 30.Alternatively, piston type swashplate compressor can be the single-head piston type swashplate compressor that comprises single head pison.
Claims (6)
1. a piston type swashplate compressor (10), comprising:
Housing (H);
Cylinder body (11,12), described cylinder body (11,12) is formed in described housing (H);
Cylinder cap (13,14), described cylinder cap (13,14) is formed in described housing (H), and described cylinder cap (13,14) is connected to the end of described cylinder body (11,12);
Running shaft (22), described running shaft (22) is supported in rotatable mode by described cylinder body (11,12);
Multiple cylinder thoraxes (28,29), described cylinder thorax (28,29) is arranged around described running shaft (22);
Multiple pistons (30), described piston (30) is contained in described cylinder thorax (29) respectively;
Swash plate (24), described swash plate (24) rotates integratedly with described running shaft (22), and described swash plate (24) engages with described piston (30); And
Multiple pressing chambers (29A), described pressing chamber (29A) is limited in described cylinder thorax (29) by described piston (30) respectively,
It is characterized in that, described piston type swashplate compressor (10) also comprises: be arranged on the multiple lid side discharge chambers (33A, 33B, 33C, 35A, 35B, 35C) in described cylinder cap (13,14); Be arranged on the multiple cylinder body side discharge chambers (40,42) in described cylinder body (11,12); Be formed as the outlet (46) through described housing (H), the refrigerant gas of compression flows to described housing (H) outside via described outlet (46); And be formed on the discharge path in described housing (H), refrigerant gas flows through described lid side discharge chamber (33A, 33B, 33C, 35A, 35B, 35C) and described cylinder body side discharge chamber (40,42) and flows to described outlet (46) from described pressing chamber (28A, 29A) via described discharge path, and
Flow through the lid side discharge chamber (33A, 33B, 33C, 35A, 35B, 35C) being communicated with described pressing chamber (28A, 29A) and flow through a cylinder body side discharge chamber (40,42) afterwards at the refrigerant gas flowing out from described pressing chamber (28A, 29A), refrigerant gas flows to another lid side discharge chamber (33A, 33B, 33C, 35A, 35B, 35C).
2. piston type swashplate compressor according to claim 1 (10), it is characterized in that, form multiple lid side discharge chambers (33A, 33B, 33C, 35A, 35B, 35C) by separating along the sense of rotation of described running shaft (22) space (28B, 29B) forming circlewise around described running shaft (22) by next door (32A, 32B, 32C, 34A, 34B, 34C).
3. piston type swashplate compressor according to claim 1 (10), it is characterized in that, form multiple cylinder body side discharge chambers (40,42) around described running shaft (22), flow to a lid side discharge chamber (33A, 33B, 33C, 35A, 35B, 35C) afterwards via described discharge path from a cylinder body side discharge chamber (40,42) at the refrigerant gas flowing out from described pressing chamber (28A, 29A), refrigerant gas flows to another cylinder body side discharge chamber (40,42).
4. piston type swashplate compressor according to claim 3 (10), is characterized in that, each cylinder body side discharge chamber (40,42) is positioned between any two adjacent cylinder thoraxes (29).
5. piston type swashplate compressor according to claim 1 (10), it is characterized in that, between described cylinder body (11,12) and described cylinder cap (13,14), be provided with liner (G), be formed with first segment discharge orifice (15F, 16F) through described liner (G), at least one the cylinder body side discharge chamber in described cylinder body side discharge chamber (40,42) is communicated with at least one the lid side discharge chamber in described lid side discharge chamber (33A, 33B, 33C, 35A, 35B, 35C) via described first segment discharge orifice (15F, 16F).
6. piston type swashplate compressor according to claim 1 (10), it is characterized in that, at described cylinder body (11, 12) with described cylinder cap (13, 14) between, be provided with valve plate (20, 21), described valve plate (20, 21) a part forms expulsion valve (15B, 16B), at described valve plate (20, 21) in, be formed with second section discharge orifice (20A, 21A), and described cylinder body side discharge chamber (40, 42) at least one the cylinder body side discharge chamber in is via described second section discharge orifice (20A, 21A) with described lid side discharge chamber (33A, 33B, 33C, 35A, 35B, at least one lid side discharge chamber 35C) is communicated with.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013066641A JP5915576B2 (en) | 2013-03-27 | 2013-03-27 | Piston type swash plate compressor |
| JP2013-066641 | 2013-03-27 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104074710A true CN104074710A (en) | 2014-10-01 |
Family
ID=51596247
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410116904.0A Pending CN104074710A (en) | 2013-03-27 | 2014-03-26 | Piston type swash plate compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20140294617A1 (en) |
| JP (1) | JP5915576B2 (en) |
| KR (1) | KR101534601B1 (en) |
| CN (1) | CN104074710A (en) |
| BR (1) | BR102014007234A2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110318973A (en) * | 2018-03-30 | 2019-10-11 | 株式会社丰田自动织机 | Piston compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR200487258Y1 (en) | 2017-08-03 | 2018-08-28 | 김태균 | Holder Bar For Crop Duster |
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| CN1170827A (en) * | 1995-11-20 | 1998-01-21 | 株式会社丰田自动织机制作所 | Piston type compressor |
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| CN1228510A (en) * | 1998-03-06 | 1999-09-15 | 株式会社丰田自动织机制作所 | Pressure-pulsation-reducing compressor |
| CN101235808A (en) * | 2007-02-02 | 2008-08-06 | 株式会社丰田自动织机 | Double-headed piston type compressor |
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| JPH0447429Y2 (en) * | 1987-05-13 | 1992-11-09 | ||
| DE4493590T1 (en) * | 1993-05-21 | 1995-06-01 | Toyoda Automatic Loom Works | Compressor with reciprocating pistons |
| JP2590662Y2 (en) * | 1993-07-12 | 1999-02-17 | 株式会社豊田自動織機製作所 | Reciprocating compressor |
| JP3266504B2 (en) * | 1996-04-19 | 2002-03-18 | 株式会社ゼクセルヴァレオクライメートコントロール | Swash plate compressor |
| JP2000104660A (en) * | 1998-09-28 | 2000-04-11 | Sanden Corp | Compressor |
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| JP4692866B2 (en) * | 2001-07-05 | 2011-06-01 | 株式会社ヴァレオサーマルシステムズ | Swash plate compressor |
| JP4663462B2 (en) * | 2005-09-21 | 2011-04-06 | サンデン株式会社 | Reciprocating compressor |
| US20070292280A1 (en) * | 2006-06-15 | 2007-12-20 | Yomg-Wan Choi | Inside and outside structures of discharging refrigerant in bi-directional swash plate type compressor |
| KR101159863B1 (en) * | 2006-07-24 | 2012-06-25 | 한라공조주식회사 | Compressor |
| JP2010013987A (en) * | 2008-07-02 | 2010-01-21 | Toyota Industries Corp | Refrigerant suction structure in piston type compressor |
| JP5783354B2 (en) * | 2011-03-07 | 2015-09-24 | サンデンホールディングス株式会社 | Compressor |
| CN103459846A (en) * | 2011-03-31 | 2013-12-18 | 株式会社丰田自动织机 | Swash-plate-type compressor |
-
2013
- 2013-03-27 JP JP2013066641A patent/JP5915576B2/en not_active Expired - Fee Related
-
2014
- 2014-03-21 US US14/221,617 patent/US20140294617A1/en not_active Abandoned
- 2014-03-26 BR BRBR102014007234-9A patent/BR102014007234A2/en not_active IP Right Cessation
- 2014-03-26 KR KR1020140035050A patent/KR101534601B1/en not_active IP Right Cessation
- 2014-03-26 CN CN201410116904.0A patent/CN104074710A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
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| KR970009844B1 (en) * | 1993-12-27 | 1997-06-18 | 이소가와 찌세이 | Reciprocating type compressor |
| CN1170827A (en) * | 1995-11-20 | 1998-01-21 | 株式会社丰田自动织机制作所 | Piston type compressor |
| JPH11173274A (en) * | 1997-12-04 | 1999-06-29 | Zexel:Kk | Variable displacement type swash plate compressor without clutch |
| CN1228510A (en) * | 1998-03-06 | 1999-09-15 | 株式会社丰田自动织机制作所 | Pressure-pulsation-reducing compressor |
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| CN110318973A (en) * | 2018-03-30 | 2019-10-11 | 株式会社丰田自动织机 | Piston compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| BR102014007234A2 (en) | 2015-08-04 |
| US20140294617A1 (en) | 2014-10-02 |
| KR20140118845A (en) | 2014-10-08 |
| JP5915576B2 (en) | 2016-05-11 |
| JP2014190238A (en) | 2014-10-06 |
| KR101534601B1 (en) | 2015-07-24 |
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Application publication date: 20141001 |