CN101806294B

CN101806294B - Piston-type compressor

Info

Publication number: CN101806294B
Application number: CN2010101142158A
Authority: CN
Inventors: 石川光世; 小林俊之
Original assignee: Toyoda Automatic Loom Works Ltd
Current assignee: Toyota Industries Corp
Priority date: 2009-02-17
Filing date: 2010-02-22
Publication date: 2012-07-18
Anticipated expiration: 2030-02-22
Also published as: CN101806294A; KR20100094322A; JP2010190093A; US20100209262A1

Abstract

A piston compressor includes first and second cylinder blocks having an inlet port and a swash plate chamber, a drive shaft having first and second guide holes, and a swash plate having first and second supply ports. The swash plate chamber communicates with the inlet port and also with the first and second guide holes via the first and second supply ports, respectively. A distance from the inlet port to the first supply port when the first supply port is moved closest to the inlet port is greater than a distance from the inlet port to the second supply port when the second supply port is moved closest to the inlet port, and the smallest flow passage area in the first supply port and the first guide hole is greater than the smallest flow passage area in the second supply port and the second guide hole.

Description

Piston compressor

Technical field

The present invention relates to a kind of piston compressor.

Background technique

Japanese utility model application publication no No.63-174579 discloses a kind of piston compressor that comprises a pair of front and rear cylinder.Front-bank rotor housing heart place therein has front-axle hole and is formed on front-axle hole a plurality of preceding cylinder thorax on every side.Similarly, rear-bank rotor housing has back axis hole and is formed on back axis hole a plurality of backs cylinder thorax on every side in heart place therein.Front-bank rotor housing and rear-bank rotor housing combine, and make front-axle hole and preceding cylinder thorax aim at back axis hole and back cylinder thorax respectively.Preceding cylinder thorax cooperates with back cylinder thorax and forms many to forward and backward cylinder thorax.Front-bank rotor housing and rear-bank rotor housing have the swash plate chamber between them.

This piston compressor also comprises a pair of forward and backward housing.Front case is bonded to front-bank rotor housing via preceding valve cell, and preceding valve cell comprises preceding expulsion valve of a plurality of reed type and the preceding suction valve of a plurality of reed type.Front case has the preceding discharge chamber that can be communicated with preceding cylinder thorax via corresponding reed type expulsion valve and the preceding suction chamber that can be communicated with preceding cylinder thorax via suction valve before the corresponding reed type.Similarly, rear case is bonded to back cylinder thorax via the back valve cell, and back valve cell comprises after a plurality of reed type suction valve behind the expulsion valve and a plurality of reed type.Rear case has the back discharge chamber that can be communicated with back cylinder thorax via expulsion valve after the corresponding reed type and the suction chamber that can be communicated with back cylinder thorax via suction valve after the corresponding reed type.

Live axle rotatably is supported on the axis hole place by front case, front-bank rotor housing and rear-bank rotor housing.Swash plate is installed on the live axle so that rotate synchronously with live axle.Swash plate has via thrust bearing and remains on bump and the cam part integrally formed with bump between front-bank rotor housing and the rear-bank rotor housing.A plurality of double-head pistons are contained in corresponding forward and backward cylinder thorax centering.When live axle rotated, the cam part cause piston of swash plate moved back and forth their corresponding forward and backward cylinder thorax centerings.Each piston is in its compression chamber and back compression chamber before this has the opposite side in the forward and backward cylinder thorax.The inlet ports that preceding cylinder thorax has radially extension therein is with the external refrigerant loop interconnections with swash plate chamber and piston compressor.Front-bank rotor housing and rear-bank rotor housing have a plurality of suction channels that connect them, and these suction channels are parallel to the axis extension of live axle and via the swash plate chamber preceding suction chamber and back suction chamber are interconnected.

According to this piston compressor, have from the suction channel of the longer path of inlet ports and be formed with bigger flow channel area.Therefore, the flow rate of the refrigerant gas of the suction channel of flowing through equates basically, and the refrigerant gas of substantially the same amount is drawn in each compression chamber.Therefore, the noise that has improved the suction efficiency of compressor and reduced compressor produces.

Some compressors do not adopt the reed type suction valve, and are to use the rotary valve that can rotate synchronously with the live axle of compressor refrigerant gas optionally is extracted into corresponding compression chamber, so that the pressure loss that prevention causes because of the reed type suction valve.Particularly, known a kind of compressor, in this compressor, the refrigerant gas in the swash plate chamber is without suction channel but passage in the bump that is formed on swash plate and the passage in being formed on live axle and be drawn in the corresponding compression chamber.More specifically, the bump of the swash plate of this compressor has the preceding supply port that connects it and supplies with port with the back, and these are supplied with ports and radially extend and be opened on the swash plate chamber.Supplying with port separates each other on the sense of rotation of swash plate.Live axle has axial bore, the preceding bullport that is communicated with preceding supply port and axial bore, the back bullport, the preceding suction bullport that is communicated with axial bore that are communicated with back supply port and axial bore and the back suction bullport that is communicated with axial bore that extends along the axial direction of live axle therein.Front-bank rotor housing has a plurality of ports that advance into that can be communicated with preceding suction bullport and corresponding preceding compression chamber therein.Rear-bank rotor housing has entry port behind can be communicated with back suction bullport and corresponding back compression chamber a plurality of therein.

In this compressor, the refrigerant gas in the swash plate chamber is drawn in the forward and backward compression chamber through forward and backward supply port, forward and backward bullport, axial bore, forward and backward suction bullport and forward and backward entry port.Therefore; Before supply with port, preceding bullport, axial bore, preceding suction bullport and advance into that port cooperates and inhalation flow path before forming; This passage is used for subsequently for intake stroke preceding compression chamber, double-head piston, with the refrigerant gas suction in the swash plate chamber before each in the compression chamber.The back is supplied with port, back bullport, axial bore, back suction bullport and back entry port and is cooperated and form the back inhalation flow path; This passage is used for subsequently for back intake stroke compression chamber, double-head piston, in each back compression chamber of the refrigerant gas suction in the swash plate chamber.

In the compressor of the type, what is also needed is, the suction in refrigerant gas to the compression chamber should be the same even with the situation of the compressor described in the aforementioned communique.Yet; In the above-mentioned compressor that the supply port rotates in the swash plate chamber; Being used for refrigerant gas is variable from the length that inlet ports flow to the passage of supplying with port, thereby can not adopt and the identical technological scheme of situation at the compressor described in the aforementioned communique.

If inlet ports is formed on when observing on the axial direction at live axle corresponding to the front-bank rotor housing at the center of the cam part of swash plate or the position of rear-bank rotor housing, then the refrigerant gas in inlet ports suction swash plate chamber is easy to spread through the rotation of swash plate.Therefore, reduced to flow into the suction efficiency of the refrigerant gas in the corresponding forward and backward compression chamber through forward and backward supply port.In order to prevent reducing of suction efficiency, inlet ports is formed in one in the front and rear cylinder, and it forms position for separating with the center of cam part when the observation on axial direction or forward or backward.Be formed on inlet ports in one in the front and rear cylinder by this way from preventing refrigerant gas and leak and the simple structure of compressor and prevent that the angle that suction efficiency reduces from being preferred.

Yet if inlet ports separates with the center of cam part when observing on the axial direction at live axle forward or backward, inlet ports is oriented near one in the forward and backward supply port and away from another person.In this case, aspect suction difference can appear between the forward and backward compression chamber.In this case, the temperature of the refrigerant gas of worrying to discharge from the lower compression chamber of suction efficiency can excessively rise, and therefore worries any one the liner premature deterioration correspondingly in the forward and backward valve cell.This liner deterioration can seriously influence the durability of compressor.In addition, difference can appear in the reaction force between the forward and backward compression chamber, thereby causes the vibration of the peace and quiet operation that seriously influences compressor.

The present invention relates to a kind of high-durability and quiet piston compressor that moves, keeps high suction efficiency simultaneously of providing.

Summary of the invention

According to one side of the present invention, a kind of piston compressor is provided, comprise first cylinder body, second cylinder body, live axle, swash plate and a plurality of double-head piston.First cylinder body has first axis hole, a plurality of first cylinder thorax and a plurality of first entry port.The first cylinder thorax is formed on around first axis hole and via corresponding first entry port and is communicated with first axis hole.Second cylinder body has second axis hole, a plurality of second cylinder thorax and a plurality of second entry port.The second cylinder thorax is formed on around second axis hole and via corresponding second entry port and is communicated with second axis hole.First cylinder body and second cylinder body combine.First cylinder body and second cylinder body form the swash plate chamber between the first cylinder thorax and the second cylinder thorax.In first cylinder body and second cylinder body one has the inlet ports that is connected to the swash plate chamber therein, so that allow in the refrigerant gas suction swash plate chamber.Live axle rotatably is supported on first axis hole and the second axis hole place by first cylinder body and second cylinder body respectively.Live axle has axial bore, the first suction bullport, second suction bullport, first bullport and second bullport therein.Axial bore extends along the axial direction of live axle.The first suction bullport is communicated with first bullport and can be communicated with first entry port of first cylinder body via axial bore.The second suction bullport is communicated with second bullport and can be communicated with second entry port of second cylinder body via axial bore.Swash plate is installed in the swash plate chamber on the live axle so that rotate with the live axle one.Swash plate has the bump that is assemblied on the live axle and the cam part integrally formed with bump.Bump has first therein and supplies with the port and the second supply port.First supplies with port is communicated with first bullport of live axle and with the swash plate chamber.Second supplies with port is communicated with second bullport of live axle and with the swash plate chamber.The first supply port and second is supplied with port and on the sense of rotation of swash plate, is separated each other.A plurality of double-head pistons are contained in the corresponding first and second cylinder thoraxes and with cam part and engage.The cam part of swash plate causes double-head piston in the corresponding first and second cylinder thoraxes, to move back and forth with the rotation of live axle.The relative head of double-head piston and the first and second cylinder thoraxes limit first compression chamber and second compression chamber respectively.First compression chamber and second compression chamber can be communicated with first entry port and second entry port respectively.First supplies with port, first bullport, axial bore, the first suction bullport and first entry port cooperates and forms first inhalation flow path, so that in allowing in the intake stroke of the double-head piston of first compression chamber each first compression chamber of the refrigerant gas suction in the swash plate chamber.Second supplies with port, second bullport, axial bore, the second suction bullport and second entry port cooperates and forms second inhalation flow path, so that in allowing in the intake stroke of the double-head piston of second compression chamber each second compression chamber of the refrigerant gas suction in the swash plate chamber.The distance of when first supplies with port and be moved near inlet ports, supplying with port from inlet ports to the first greater than when second supplies with port and is moved near inlet ports from the distance of inlet ports to the second supply port.Minimal flow aisle spare in the first supply port and first bullport is greater than the minimal flow aisle spare in the second supply port and second bullport.

According to below in conjunction with accompanying drawing, the for example description of clear principle of the present invention, it is obvious that others of the present invention and advantage will become.

Description of drawings

To present description and accompanying drawing preferred embodiment, can understand the present invention and purpose and advantage with reference to following best.

Fig. 1 shows the longitudinal sectional view of the piston compressor of first embodiment of the invention;

Fig. 2 shows the local longitudinal sectional view of the piston compressor of Fig. 1;

Fig. 3 shows the local longitudinal sectional view of piston compressor second embodiment of the invention;

Fig. 4 shows the local longitudinal sectional view according to the piston compressor of the 3rd mode of execution of the present invention;

Fig. 5 shows the local longitudinal sectional view according to the piston compressor of the 4th mode of execution of the present invention;

Fig. 6 shows the local longitudinal sectional view according to the piston compressor of the 5th mode of execution of the present invention;

Fig. 7 shows the partial plan layout of forward and backward cylinder thorax of the piston compressor of Fig. 6;

Fig. 8 shows the partial plan layout according to the forward and backward cylinder thorax of the piston compressor of the 6th mode of execution of the present invention;

Fig. 9 shows the elevation according to the swash plate of the piston compressor of the 7th mode of execution of the present invention, shows the part of swash plate among the figure with cross section; And

Figure 10 shows the elevation according to the swash plate of the piston compressor of the 8th mode of execution of the present invention, shows the part of swash plate among the figure with cross section.

Embodiment

Piston compressor according to first to the 8th mode of execution of the present invention is described below with reference to accompanying drawings.

With reference to Fig. 1, the piston compressor of first mode of execution is the fixed displacement type slant plate type compressor.This compressor comprises front-bank rotor housing 1 and rear-bank rotor housing 3.Front-bank rotor housing 1 has front-axle hole 1A with the mode that connects it and is formed on front-axle hole 1A a plurality of preceding cylinder thorax 1B on every side.Similarly, rear-bank rotor housing 3 has back axis hole 3A with the mode that connects it and is formed on back axis hole 3A a plurality of back cylinder thorax 3B on every side.Front-bank rotor housing 1 combines with rear-bank rotor housing 3, makes corresponding with them the respectively back axis hole 3A of front-axle hole 1A and preceding cylinder thorax 1B aim at back cylinder thorax 3B.Preceding cylinder thorax 1B cooperates with back cylinder thorax 3B and forms many to forward and backward cylinder thorax 1B and 3B.Front-bank rotor housing 1 and rear-bank rotor housing 3 have O type circle 2 between them.Front-bank rotor housing 1 and rear-bank rotor housing 3 also have swash plate chamber 25 between the first cylinder thorax 3B and the second cylinder thorax 1B.It should be noted that the left-hand side of Fig. 1 and right-hand side correspond respectively to the front and rear of compressor.

This compressor also comprises front case 7 and rear case 11.Front case 7 is bonded to front-bank rotor housing 1 via preceding valve cell 5.Preceding valve cell 5 comprises: valve plate 51, and it has a plurality of discharge port 51B that connect it; A plurality of reed type expulsion valve 52A, they can be operated to open and close and discharge port 51B; And a plurality of positioning work piece 53A, its restriction expulsion valve 52A opens.Valve plate 51 is formed with the liner (not shown) on a side of its contiguous front-bank rotor housing 1.Liner forms through covering the coat with rubber material.Front case 7 has the discharge chamber 7A that can be communicated with preceding cylinder thorax 1B via corresponding expulsion valve 52A therein.Front case 7 and front-bank rotor housing 1 have O type circle 4 between them.

In a similar fashion, rear case 11 is bonded to rear-bank rotor housing 3 via back valve cell 9.Back valve cell 9 comprises: valve plate 91, and it has a plurality of discharge port 91B that connect it; A plurality of reed type expulsion valve 92A, they can be operated to open and close and discharge port 91B; And a plurality of positioning work piece 93A, its restriction expulsion valve 92A opens.Valve plate 91 is formed with the liner (not shown) on a side of its contiguous rear-bank rotor housing 3.Liner forms through covering the coat with rubber material.Rear case 11 has the discharge chamber 11A that can be communicated with back cylinder thorax 3B via corresponding expulsion valve 92A therein.Rear case 11 and rear-bank rotor housing 3 have O type circle 6 between them.Housing 7,11 and

cylinder body

1,3 are tightened together by a plurality of bolts 8 (only illustrating).

Discharge chamber

7A, 11A are communicated with single discharge chamber (not shown).

Front case 7 has the front-axle hole 7B that connects it.Live axle 13 rotatably is supported on

axis hole

1A, 3A and 7B place by

cylinder body

1,3 and front case 7 respectively.Swash plate 27 is installed in swash plate chamber 25 on the live axle 13 so that rotate with live axle 13 one.Swash plate 27 has via thrust bearing 31A, 31B and remains on bump 27A and the cam part 27B integrally formed with bump 27A between front-bank rotor housing 1 and the rear-bank rotor housing 3.Bump 27A is assemblied on the live axle 13.A plurality of double-head pistons 17 are contained in corresponding forward and backward cylinder thorax among 1B and the 3B and via many forward and backward sliding

shoes

18A and 18B being engaged with cam part 27B respectively.When live axle 13 rotation, the cam part 27B cause piston 17 of swash plate 27 moves back and forth in to 1B and 3B at forward and backward cylinder thorax of their correspondences with 18B and respectively to forward and backward sliding shoes 18A via many.

The relative head of each piston 17 is 19A of compression chamber and the back 19B of compression chamber before this limits in to forward and backward cylinder thorax 1B and 3B.Front-bank rotor housing 1 has the inlet ports 1C that radially extends and be connected to swash plate chamber 25 therein, so that allow in the refrigerant gas suction swash plate chamber 25 in the external refrigerant loop of compressor.

With reference to Fig. 2, the bump 27A of swash plate 27 has the preceding supply port 27C that connects it and supplies with port 27D with the back, and these supply ports radially extend in opposite direction and are communicated with swash plate chamber 25.That is preceding supply port 27C and back are supplied with port 27D and are separated angularly each other with the angle of the about 180 degree sense of rotation along swash plate 27.When the back supply with that port 27D moves and the distance of supplying with port 27D to the back from inlet ports 1C during near inlet ports 1C greater than current supply port 27C moves the distance from inlet ports 1C to preceding supply port 27C during near inlet ports 1C, and the flow channel area of port 27D when in cross section, observing supplied with greater than the flow channel area of preceding supply port 27C when the observation in cross section in the back.In other words; Current supply port 27C move and during near inlet ports 1C the distance from inlet ports 1C to preceding supply port 27C be shorter than when the back and supply with that port 27D moves and supply with the distance of port 27D during near inlet ports 1C from inlet ports 1C to the back, and the flow channel area of preceding supply port 27C when in cross section, observing is less than the flow channel area of back supply port 27D when the observation in cross section.Confirm that the back supplies with the difference of the flow channel area between port 27D and the preceding supply port 27C so that the difference that the suction of the 19A of compression chamber before each is flowed with the suction of its corresponding back 19B of compression chamber between mobile is reduced to minimum.

Live axle 13 has axial bore 13A, the preceding bullport 13B that is communicated with preceding supply port 27C and axial bore 13A, the back bullport 13C, the preceding suction bullport 13D that is communicated with axial bore 13A that are communicated with back supply port 27D and axial bore 13A and the back suction bullport 13E that is communicated with axial bore 13A that extends along the axial direction of live axle 13 therein.Preceding bullport 13B has the identical diameter with preceding supply port 27C, and then bullport 13C has the identical diameter with back supply port 27D.That is; When back bullport 13C move and during near inlet ports 1C from the distance of inlet ports 1C bullport 13C to the back greater than current bullport 13B moves the distance from inlet ports 1C to preceding bullport 13B during near inlet ports 1C, and the flow channel area of back bullport 13C when in cross section, observing is greater than the flow channel area of preceding bullport 13B when the observation in cross section.In other words; Current bullport 13B move and during near inlet ports 1C the distance from inlet ports 1C to preceding bullport 13B be shorter than as back bullport 13C and move and the distance from inlet ports 1C to back bullport 13C during near inlet ports 1C, and the flow channel area of preceding bullport 13B when in cross section, observing less than after the flow channel area of bullport 13C when the observation in cross section.Preceding suction bullport 13D and back suction bullport 13E have substantially the same flow channel area.Therefore, be arranged in the part formation rotary valve of front-axle hole 1A and back axis hole 3A in the live axle 13, the structure that this has improved suction efficiency and has simplified compressor.

Front-bank rotor housing 1 has a plurality of ports 21 that advance into that radially extend and can be communicated with the corresponding preceding 19A of compression chamber from front-axle hole 1A therein.The preceding suction bullport 13D of live axle 13 can be through the rotation of live axle 13 with respectively advance into port 21 and be communicated with.Rear-bank rotor housing 3 has a plurality of backs entry port 23 that axis hole 3A radially extends and can be communicated with the corresponding back 19B of compression chamber from the back therein.The back suction bullport 13E of live axle 13 can be communicated with each back entry port 23 through the rotation of live axle 13.Advance into port 21 and have substantially the same flow channel area with back entry port 23.

Therefore; Before supply with port 27C, preceding bullport 13B, axial bore 13A, preceding suction bullport 13D and advance into port 21 cooperate and form before inhalation flow path so that allow subsequently in the intake stroke of the piston 17 that moves backward the refrigerant gas suction in the swash plate chamber 25 before each among the 19A of compression chamber.The back is supplied with port 27D, back bullport 13C, axial bore 13A, back suction bullport 13E and back entry port 23 and is cooperated and form the back inhalation flow path, so that allow subsequently in the intake stroke of the piston that moves forward 17 among each back 19B of compression chamber of the refrigerant gas suction in the swash plate chamber 25.In the compressor of first mode of execution, the flow channel area that port 27D and back bullport 13C are supplied with in the back is respectively greater than the flow channel area of preceding supply port 27C and preceding bullport 13B.

When the compressor of Fig. 1 was used for Vehicular air-conditioning apparatus, its single discharge chamber (not shown) was connected to the condenser (not shown) in the external refrigerant loop that has other parts such as expansion valve and vaporizer (each person is not shown) therein via the pipeline (not shown).Vaporizer is connected to inlet ports 1C via the pipeline (not shown).Live axle 13 is through at the belt of transmission between motor and the belt wheel or be installed in the magnetic clutch on the live axle 13 and driven by the motor (not shown).

When live axle 13 is rotated by engine-driving, swash plate 27 and the rotation of live axle 13 one, thereby cause each piston 17 its corresponding forward and backward cylinder thorax to 1B and 3B in to move back and forth by the definite running length of the inclination of swash plate 27.In conjunction with the to-and-fro motion of piston 17, form fluid and be communicated with advancing between the port 21 at preceding suction bullport 13D, and in the back suction bullport 13E with afterwards also form fluid between the entry port 23 and be communicated with.Therefore, swash plate chamber 25 is communicated with the preceding 19A of compression chamber via preceding inhalation flow path, and is communicated with the back 19B of compression chamber fluid via the back inhalation flow path.Discharging chamber 7A before compressed refrigerant is discharged to respectively in the preceding 19A of compression chamber and the back 19B of compression chamber discharges among the chamber 11A with the back.Discharge before being discharged to that the refrigerant gas of chamber 7A and back discharging chamber 11A is sent to condenser via single discharge chamber and pipeline subsequently and turn back to the inlet ports 1C of compressor via expansion valve and vaporizer.Therefore, accomplish the air conditioning circulation.

In compressor; Be formed on the axial the place ahead at center that inlet ports 1C in the front-bank rotor housing 1 is positioned at the cam part 27B of swash plate 27, as shown in Figure 2, thus refrigerant gas is not easy to diffusion; Said diffusion causes because of the rotation of swash plate 27, and the result has kept high suction efficiency.The layout of inlet ports 1C helps to prevent that refrigerant gas from leaking and simplifying the structure of compressor.

Supply with in the compressor of flow channel area greater than this mode of execution of the flow channel area of preceding supply port 27C of port 27D in the back, the difference between the suction of the preceding 19A of compression chamber suction mobile and the back 19B of compression chamber is flowed is reduced to minimum.Thereby, in the past the 19A of the compression chamber refrigerant gas of discharging be reduced to minimum from the temperature difference between the refrigerant gas of the back 19B of compression chamber discharge, thereby prevented any one the premature deterioration in the liner of valve cell 5 and 9 and/or in O type circle 4 and 6.Reaction force difference between preceding 19A of compression chamber and the back 19B of compression chamber also is reduced to minimum, has therefore successfully prevented the vibration that produces owing to this difference.

Therefore, the compressor of this mode of execution provides high-durability and quiet operation, keeps high suction efficiency simultaneously.

To piston compressor second embodiment of the invention be described with reference to Fig. 3.The compressor of second mode of execution is substantially the same with the compressor of first mode of execution, because the flow channel area of the back supply port 27D of the bump 27A of swash plate 27 is greater than the flow channel area of preceding supply port 27C.The difference of second mode of execution and first mode of execution is, has the identical flow channel area with back bullport 13C corresponding to the preceding bullport 13F of the preceding bullport 13B of first mode of execution.All the other aspects of the structure of second mode of execution are substantially the same with first mode of execution.

Supply with in the compressor of flow channel area greater than second mode of execution of the flow channel area of preceding supply port 27C of port 27D in the back, the flow resistance of the refrigerant gas that port 27D is supplied with in the back of flowing through---it is more farther than preceding supply port 27C from inlet ports 1C---is less than the flow resistance of supplying with the refrigerant gas of port 27C before flowing through.

Therefore, the compressor of second mode of execution provides the advantageous effects substantially the same with first mode of execution.

To the piston compressor according to the 3rd mode of execution of the present invention be described with reference to Fig. 4.The compressor of the 3rd mode of execution is substantially the same with the compressor of first mode of execution, because the flow channel area of back bullport 13C---it is more farther than preceding bullport 13B from inlet ports 1C---is greater than the flow channel area of preceding bullport 13B.The difference of the 3rd mode of execution and first mode of execution is, has and the identical flow channel area of port 27D is supplied with in the back corresponding to the preceding supply port 27E of the preceding supply port 27C of first mode of execution.All the other aspects of the structure of the 3rd mode of execution are substantially the same with first mode of execution.

In the compressor of flow channel area greater than the 3rd mode of execution of the flow channel area of preceding bullport 13B of back bullport 13C, the flow resistance of the refrigerant gas of the back bullport 13C---it is more farther than preceding bullport 13B from inlet ports 1C---that flows through is less than the flow resistance of the refrigerant gas of bullport 13B before flowing through.

Therefore, the compressor of the 3rd mode of execution provides the advantageous effects substantially the same with first mode of execution.

To the piston compressor according to the 4th mode of execution of the present invention be described with reference to Fig. 5.In the 4th mode of execution, the flow channel area of back suction bullport 13E---it is farther corresponding to the preceding suction bullport 13G of the preceding suction bullport 13D of first mode of execution from inlet ports 1C ratio---is greater than the flow channel area of preceding suction bullport 13G.That is; When live axle 13 rotations; From inlet ports 1C through first supply with port 27D suction bullport 13E to the back the shortest flow passage be longer than from inlet ports 1C and supply with the shortest flow passage of port 27C through second to preceding suction bullport 13G, and the flow channel area of the flow channel area of bullport 13E greater than preceding suction bullport 13G aspirated in the back.All the other aspects of the structure of the 4th mode of execution are substantially the same with first mode of execution.

In the compressor of flow channel area greater than the 4th mode of execution of the flow channel area of preceding suction bullport 13G of back suction bullport 13E, the flow resistance of the refrigerant gas of the back suction bullport 13E---it is more farther than preceding suction bullport 13G from inlet ports 1C---that flows through is less than the flow resistance of the refrigerant gas of suction bullport 13G before flowing through.

Therefore, the compressor of the 4th mode of execution provides the advantageous effects substantially the same with first mode of execution.

To the piston compressor according to the 5th mode of execution of the present invention be described with reference to Fig. 6 and 7.In the 5th mode of execution, each back entry port 23---its from inlet ports 1C than corresponding to first mode of execution advance into port 21 to advance into port 24 farther---the flow channel area greater than the flow channel area that advances into port 24.Respectively advance into port 24 rounded well format when the time from cross-sectional view as shown in Figure 7, and the also rounded well format of each back entry port 24.All the other aspects of the structure of the 5th mode of execution are substantially the same with first mode of execution.

In the compressor of flow channel area greater than the 5th mode of execution of the flow channel area that advances into port 24 of back entry port 23, the flow resistance of the refrigerant gas of the back entry port 23---it is farther that it advances into port 24 from inlet ports 1C ratio---of flowing through advances into the flow resistance of the refrigerant gas of port 24 less than flowing through.The back entry port 23 that circular port provided with advance into port 24 and back entry port 23 and compare the flow resistance of the refrigerant gas of can reduce to flow through these

entry ports

23 and 24 with the situation that advances into the hole of port 24 and provide by other shape with non-circular shape.

Therefore, the compressor of the 5th mode of execution provides the advantageous effects substantially the same with first mode of execution.

In addition; Not only have difference between the flow channel area of the back flow channel area of supplying with port 27D and back bullport 13C and preceding supply port 27C and preceding bullport 13B, and afterwards also there is difference in each between entry port 23 and the corresponding flow channel area that advances into port 24.Therefore, significantly realized advantageous effects of the present invention.

To the piston compressor according to the 6th mode of execution of the present invention be described with reference to Fig. 8.In the 6th mode of execution, form by rounded hole when in cross section as shown in Figure 8, observing than corresponding port 26 each the farther back entry port 23 that advance into from inlet ports 1C.Advancing into port 26 forms by when in cross section as shown in Figure 8, observing, being microscler hole.When from the end on observation of live axle 13, back entry port 23 is formed with the diameter substantially the same with the length that advances into port 26.All the other aspects of the structure of the 6th mode of execution are substantially the same with first mode of execution.

In this compressor, to carry out in identical correct time, this helps the generation of constrained vibration to the intake stroke of piston 17 in the preceding 19A of compression chamber and the back 19B of compression chamber.

To the piston compressor according to the 7th mode of execution of the present invention be described with reference to Fig. 9.In the 7th mode of execution, be formed with jut 28A and depressed part 28B corresponding to the back supply port 28 of the back supply port 27D of first mode of execution.Particularly, jut 28A is formed on the outer surface of bump 27A, this outer surface by first supply with port 28 opening form with respect to the tail side of the sense of rotation R of swash plate 27.Depressed part 28B is formed on the outer surface of bump 27A, this outer surface by first supply with port 28 opening form with respect to the relative front side of the sense of rotation R of swash plate 27.All the other aspects of the structure of the 7th mode of execution are substantially the same with first mode of execution.

In the compressor of the 7th mode of execution, during the rotation of swash plate 27, refrigerant gas 32 can easily flow into from inlet ports 1C than the farther back supply port 28 of preceding supply port 27C in.

Therefore, the compressor of the 7th mode of execution provides the advantageous effects substantially the same with first mode of execution.

To the piston compressor according to the 8th mode of execution of the present invention be described with reference to Figure 10.In the 8th mode of execution, corresponding to the back supply port 30 of the back supply port 27D of first mode of execution inclined, so that refrigerant gas 32 is directed among the axial bore 13A through the rotation of swash plate 27 from bump 27A.All the other aspects of the structure of the 8th mode of execution are substantially the same with first mode of execution.

In the compressor of the 8th mode of execution, similar with the 7th mode of execution, during the rotation of swash plate 27, refrigerant gas 32 can easily flow into from inlet ports 1C than the farther back supply port 30 of preceding supply port 27C in.

Therefore, the compressor of the 8th mode of execution provides the advantageous effects substantially the same with first mode of execution.

In the context of above-mentioned first to the 8th mode of execution, described the present invention, but the present invention is not limited to these mode of executions.Obviously, the present invention can implement with the following variety of way of illustration.

Though inlet ports 1C is formed in the front-bank rotor housing 1 in the above-described embodiment, inlet ports can be formed in the rear-bank rotor housing.In this case, above-mentioned distance relation is put upside down.

Claims

1. piston compressor comprises:

First cylinder body (3); It has first axis hole (3A), a plurality of first cylinder thorax (3B) and a plurality of first entry port (23); Wherein, the said first cylinder thorax (3B) is formed on said first axis hole (3A) and is communicated with said first axis hole (3A) on every side and via corresponding said first entry port (23);

Second cylinder body (1); It has second axis hole (1A), a plurality of second cylinder thoraxes (1B) and a plurality of second entry port (21,24,26); Wherein, The said second cylinder thorax (1B) is formed on said second axis hole (1A) and is communicated with said second axis hole (1A) on every side and via corresponding said second entry port (21,24,26); Said first cylinder body (3) and said second cylinder body (1) combine; Said first cylinder body (3) and said second cylinder body (1) form swash plate chamber (25) between said first cylinder thorax (3B) and the said second cylinder thorax (1B), one in said first cylinder body (3) and said second cylinder body (1) has the inlet ports (1C) that is connected to said swash plate chamber (25) therein, so that allow in refrigerant gas (32) the said swash plate chamber of suction (25);

Live axle (13); It is respectively by said first cylinder body (3) with said second cylinder body (1) is supported on said first axis hole (3A) with rotatable mode and said second axis hole (1A) is located; Said live axle (13) have therein axial bore (13A), the first suction bullport (13E), the second suction bullport (13D, 13G), first bullport (13C) and second bullport (13B, 13F); Wherein, Said axial bore (13A) extends along the axial direction of said live axle (13), and the said first suction bullport (13E) is communicated with said first bullport (13C) and can be communicated with first entry port (23) of said first cylinder body (3) via said axial bore (13A), the said second suction bullport (13D; 13G) via said axial bore (13A) and the said second bullport (13B; 13F) be communicated with and can be communicated with second entry port (21,24,26) of said second cylinder body (1);

Swash plate (27), it is installed in said swash plate chamber (25), and said live axle (13) is gone up so that rotate with said live axle (13) one, wherein; Said swash plate (27) has the bump (27A) that is assemblied on the said live axle (13) and the cam part (27B) integrally formed with said bump (27A), and said bump (27A) has first therein and supplies with port (27D, 28; 30) and second supply with port (27C, 27E), said first supplies with port (27D; 28,30) be communicated with first bullport (13C) of said live axle (13) and with said swash plate chamber (25), said second supplies with port (27C; 27E) with the second bullport (13B of said live axle (13); 13F) and with said swash plate chamber (25) be communicated with, said first supplies with port (27D, 28; 30) and said second supply with port (27C 27E) separates each other on the sense of rotation (R) of said swash plate (27); And

A plurality of double-head pistons (17); It is contained in the corresponding said first and second cylinder thorax (1B; Engage 3B) and with said cam part (27B), wherein, said cam part (27B) causes said double-head piston (17) at the corresponding said first and second cylinder thorax (1B with the rotation of said live axle (13); Move back and forth 3B); The head opposite of said double-head piston (17) and the said first and second cylinder thoraxes (1B 3B) limits first compression chamber (19B) and second compression chamber (19A) respectively, said first compression chamber (19B) and said second compression chamber (19A) respectively can with said first entry port (23) and said second entry port (21; 24,26) be communicated with;

Wherein, said first supply with port (27D, 28; 30), said first bullport (13C), said axial bore (13A), the said first suction bullport (13E) form first inhalation flow path (13A, 13C, 13E with said first entry port (23) cooperation; 23,27D, 28; 30); So that allow in the intake stroke of the said double-head piston (17) of said first compression chamber (19B), in each said first compression chamber (19B) of said refrigerant gas (32) suction in the said swash plate chamber (25), and

Wherein, said second supply with port (27C, 27E), said second bullport (13B, 13F), said axial bore (13A), the said second suction bullport (13D; 13G) form second inhalation flow path (13A, 13B with said second entry port (21,24,26) cooperation; 13D, 13F, 13G, 21; 24,26,27C; 27E), so that in allowing in the intake stroke of the said double-head piston (17) of said second compression chamber (19A) each said second compression chamber (19A) of said refrigerant gas (32) suction in the said swash plate chamber (25)

Said piston compressor is characterised in that

Supply with that port (27D, 28,30) moves and supply with port (27D from said inlet ports (1C) to said first during near said inlet ports (1C) when said first; 28,30) distance is greater than supplying with port (27C 27E) moves and supplies with port (27C from said inlet ports (1C) to said second during near said inlet ports (1C) when said second; Distance 27E), wherein, said first supplies with port (27D; 28; 30) and the minimal flow aisle spare in said first bullport (13C) supply with port greater than said second (27C be 27E) with said second bullport (13B, the minimal flow aisle spare in 13F).

2. piston compressor as claimed in claim 1; It is characterized in that the corresponding said flow channel area in said first supply port (27D) and said first bullport (13C) is greater than the said flow channel area in said second supply port (27C) and said second bullport (13B).

3. piston compressor as claimed in claim 1 is characterized in that, the flow channel area of said first bullport (13C) equals the flow channel area of said second bullport (13F).

4. piston compressor as claimed in claim 1 is characterized in that, the flow channel area of the said first supply port (27D) equals the flow channel area of the said second supply port (27E).

5. like each described piston compressor in the claim 1 to 4; It is characterized in that; When said live axle (13) rotates; Supplying with port (27D) to the shortest flow passage of the said first suction bullport (13E) from said inlet ports (1C) through said first is longer than from the shortest flow passage of said inlet ports (1C) through the said second supply port (27C) to the said second suction bullport (13G); And the flow channel area of the said first suction bullport (13E) is greater than the flow channel area of the said second suction bullport (13G).

6. like each described piston compressor in the claim 1 to 4; It is characterized in that; When said live axle (13) rotates; Supplying with port (27D) to the flow passage of each said first entry port (23) from said inlet ports (1C) through said first is longer than from the flow passage of said inlet ports (1C) through the said second supply port (27C) to corresponding said second entry port (24); And the flow channel area of said first entry port (23) is greater than the flow channel area of said second entry port (24).

7. like each described piston compressor in the claim 1 to 4, it is characterized in that, when in cross section, observing, the rounded well format of each person in said first and second entry ports (23,24).

8. like each described piston compressor in the claim 1 to 4; It is characterized in that; When said live axle (13) rotates; Supplying with port (27D) to the flow passage of each said first entry port (23) from said inlet ports (1C) through said first is longer than from the flow passage of said inlet ports (1C) through the said second supply port (27C) to corresponding said second entry port (26); And said first entry port (23) is rounded well format when in cross section, observing, and said second entry port (26) is the elongated hole form when in cross section, observing.

9. like each described piston compressor in the claim 1 to 4; It is characterized in that; On the outer surface of said bump (27A), be formed with jut (28A), said jut (28A) said first supply with port (28) opening, form with respect to the tail side of the sense of rotation (R) of said swash plate (27).

10. like each described piston compressor in the claim 1 to 4; It is characterized in that; Said first supplies with the inclined of port (30) from said bump (27A), so that through the rotation of said swash plate (27) said refrigerant gas (32) is directed in the said axial bore (13A).