DE102020108344A1 - Piston compressor - Google Patents

Abstract

A reciprocating compressor has a movable body (10) having a second communication passage (41) having a front end edge (61) on a front side in a rotating direction of the movable body (10) and a rear end edge (63) on a rear side in the direction of rotation relative to the leading end edge (61). The front end edge (61) has a first edge portion (61a) that faces a first communication passage (22a to 22f) when a flow rate of refrigerant discharged from a compression chamber (45a to 45f) into a discharge chamber (29), is maximum, and a second edge portion (61b) facing the first communication passage (22a to 22f) when the flow rate of the refrigerant is less than the maximum flow rate. The first edge portion (61a) is located on the rear side in the rotating direction relative to the second edge portion (61b).

Description

The present disclosure relates to a reciprocating compressor.

Technical background

Japanese Patent Application Publication No. H05-306680 discloses a known reciprocating compressor (hereinafter simply “compressor”). The compressor has a housing, a drive shaft, a fixed swash plate, a plurality of pistons, a discharge valve, a movable body, and a control valve.

The housing has a cylinder block. The cylinder block has a plurality of cylinder bores and a plurality of first communication passages that are in communication with a plurality of compression chambers. The housing further has a discharge chamber, a swash plate chamber, a shaft hole and a control pressure chamber. A refrigerant with a suction pressure is introduced into the swash plate chamber from the outside of the compressor. As a result, the swash plate chamber has a suction pressure region and has a pressure lower than a pressure of the discharge chamber. The swash plate chamber is in communication with the shaft hole. The control pressure chamber is at a control pressure.

The drive shaft is rotatably supported in the shaft hole. The fixed swash plate is rotatable in the swash plate chamber by rotation of the rotating shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft. Each of the pistons forms the compression chamber in the cylinder bore and is coupled to the fixed swash plate. A discharge valve is provided between the compression chamber and the discharge chamber which, while a diaphragm valve is used, allows a refrigerant in the compression chamber to be discharged into the discharge chamber.

The drive shaft is inserted through the movable body. Accordingly, the movable body is provided for the drive shaft and is arranged in the shaft hole. The movable body separates the shaft hole from the control pressure chamber. The movable body rotates together with the drive shaft in the shaft hole and is movable relative to the drive shaft in a direction of an axis of the drive shaft in accordance with the control pressure. Furthermore, a second communication passage is formed in an outer peripheral surface of the movable body. The second connection passage extends in a circumferential direction of the movable body and is intermittently communicated with each of the first connection passages by the rotation of the drive shaft. The control valve sets the control pressure.

In the compressor, the fixed swash plate is rotated by the rotation of the drive shaft, so that the piston reciprocates in the cylinder bore between a top dead center and a bottom dead center. When the piston positioned at the top dead center starts moving to the bottom dead center, the compression chamber goes into a re-expansion stroke in which the refrigerant that remains in the compression chamber re-expands. The first connection passage communicates with the second connection passage, so that the compression chamber changes from the re-expansion stroke to a suction stroke. In this situation, the second communication passage allows the refrigerant in the shaft hole, that is, the swash plate chamber, to be introduced into the compression chamber through the first communication passage. While the piston moves from bottom dead center to top dead center, the compression chamber is in a compression stroke in which the introduced refrigerant is compressed, and then changes to a discharge stroke in which the compressed refrigerant is discharged into the discharge chamber.

In the compressor, a connection angle around the axis of the drive shaft formed by the second connection passage and the first connection passage communicating with the second connection passage changes per one rotation of the drive shaft according to a position of the movable body relative to the drive shaft in FIG the direction of the axis of the drive shaft. With this configuration, in the compressor, the flow rate of the refrigerant that is introduced into the compression chamber is changed, so that the flow rate of the refrigerant that is discharged from the compression chamber into the discharge chamber is changed.

When the flow rate of the refrigerant discharged from the compression chamber into the discharge chamber is at a maximum (hereinafter, "at the maximum flow rate"), the refrigerant discharged from the compression chamber into the discharge chamber is at a high pressure, and also the refrigerant that remains in the compression chamber is at a high pressure. For this reason, if the first communication passage and the second communication passage communicate with each other before the pressure of the refrigerant remaining in the compression chamber becomes lower than the pressure of the suction pressure region through the re-expansion stroke, the refrigerant flowing in the Compression chamber remains, rearward from the first communication passage to the second communication passage, and thus to the suction pressure region side.

The piston uses the pressure in the compression chamber as part of the force to move from top dead center to bottom dead center while the compressor is operating. When the refrigerant remaining in the compression chamber flows backward to the second communication passage and the pressure in the compression chamber is thus greatly reduced, it becomes difficult for the piston to move from the top dead center to the bottom dead center. This requires a large driving force to rotate the drive shaft to move the piston. Since the refrigerant remaining in the compression chamber flows backward to the suction pressure region side, the pressure on the suction pressure region side significantly fluctuates and the amount of suction pulsation increases.

The present disclosure is made in view of the problem described above, and is directed to providing a reciprocating compressor that does not require a large drive force for rotation of a drive shaft and suppresses suction pulsation that may occur while the reciprocating compressor is in operation.

SUMMARY

According to one aspect of the present disclosure, there is provided a reciprocating compressor that has a housing, a drive shaft, a fixed swash plate, a plurality of pistons, a discharge valve, a movable body, and a control valve. The housing has a cylinder block, a discharge chamber, a swash plate chamber and a shaft hole. The cylinder block has a plurality of cylinder bores and a plurality of first communication passages. The drive shaft is rotatably supported through the shaft hole. The fixed swash plate is designed to rotate in the swash plate chamber by rotation of the drive shaft, and has a constant inclination angle with respect to a plane that is perpendicular to the drive shaft. The plurality of pistons are coupled to the fixed swash plate. Each of the pistons is received in the corresponding cylinder bore and forms a compression chamber in the cylinder bore. The compression chamber is in communication with the first communication passage. The discharge valve is configured to discharge refrigerant from the compression chamber into the discharge chamber. The movable body is provided for the drive shaft and is arranged in the shaft hole. The movable body is rotatable together with the drive shaft and is movable relative to the drive shaft in a direction of an axis of the drive shaft according to a control pressure. The movable body has a second communication passage that extends in a circumferential direction of the movable body and is intermittently connected to the first communication passage by the rotation of the drive shaft, so that the refrigerant is introduced into the compression chamber through the first communication passage, wherein a Flow rate of the refrigerant discharged from the compression chamber into the discharge chamber changes according to a position of the movable body in the direction of the axis of the drive shaft. The control valve is designed to control the control pressure. The second communication passage has: a front end edge located on a front side in a rotating direction of the movable body; and a rear end edge located on a rear side in the rotating direction relative to the front end edge. The front end edge has: a first edge portion that faces the first communication passage when the flow rate of the refrigerant discharged from the compression chamber into the discharge chamber is at a maximum flow rate; and a second edge portion facing the first communication passage when the flow rate of the refrigerant discharged from the compression chamber into the discharge chamber is less than the maximum flow rate. The first edge portion is located on the rear side in the rotating direction relative to the second edge portion.

Other aspects and advantages of the present disclosure will become apparent from the following description taken together with the accompanying drawings, which illustrate, by way of example, principles of the present disclosure.

Figure list

• 1 ist eine Querschnittsansicht eines Kolbenkompressors gemäß einem ersten Ausführungsbeispiel bei einer minimalen Strömungsrate;
• 2 ist eine Querschnittsansicht des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel bei einer maximalen Strömungsrate;
• 3 ist eine Explosionsansicht einer Antriebswelle, beweglicher Körper und dergleichen des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel;
• 4 ist eine Querschnittsansicht eines Deckels des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel;
• 5 ist eine vergrößerte Querschnittsansicht des Deckels des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel entlang Linie C-C in 4;
• 6 ist eine vergrößerte Vorderansicht eines ersten beweglichen Körpers des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel, wenn der erste bewegliche Körper von der vorderen Seite des Kompressors angesehen wird;
• 7 ist eine vergrößerte Rückansicht eines zweiten beweglichen Körpers des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel, wenn der zweite bewegliche Körper von der hinteren Seite des Kompressors angesehen wird;
• 8 ist eine vergrößerte Querschnittsansicht eines Hauptteils des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel bei der minimalen Strömungsrate, wobei die Querschnittsansicht die Antriebswelle, die beweglichen Körper und dergleichen darstellt;
• 9 ist eine vergrößerte Querschnittsansicht eines Hauptteils des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel bei der maximalen Strömungsrate, wobei die Querschnittsansicht die Antriebswelle, die beweglichen Körper und dergleichen darstellt;
• 10 ist eine vergrößerte Querschnittsansicht eines Hauptteils des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel entlang Linie A-A in 1;
• 11 ist eine vergrößerte Querschnittsansicht eines Hauptteils des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel und stellt einen Zustand dar, in dem die beweglichen Körper sich von den Positionen, bei denen die beweglichen Körper in 1 dargestellt sind, weiter nach hinten bewegt haben, und ist ähnlich zu 10;
• 12 ist eine vergrößerte Querschnittsansicht eines Hauptteils des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel entlang Linie B-B in 2;
• 13 ist eine schematische Zeichnung des ersten beweglichen Körpers des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel und stellt eine Positionsbeziehung zwischen dem ersten beweglichen Körper und einem ersten Verbindungsdurchgang bei der minimalen Strömungsrate dar;
• 14 ist eine schematische Zeichnung des ersten beweglichen Körpers des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel und stellt eine Positionsbeziehung zwischen dem ersten beweglichen Körper und dem ersten Verbindungsdurchgang bei einer mittleren Strömungsrate dar;
• 15 ist eine schematische Zeichnung des ersten beweglichen Körpers des Kolbenkompressors gemäß dem ersten Ausführungsbeispiel und stellt eine Positionsbeziehung zwischen dem ersten beweglichen Körper und dem ersten Verbindungsdurchgang bei der maximalen Strömungsrate dar;
• 16 ist eine Seitenansicht eines ersten beweglichen Körpers eines Kolbenkompressors gemäß einem zweiten Ausführungsbeispiel;
• 17 ist eine Seitenansicht eines ersten beweglichen Körpers eines Kolbenkompressors gemäß einem dritten Ausführungsbeispiel;
• 18 ist eine Seitenansicht eines ersten beweglichen Körpers eines Kolbenkompressors gemäß einem vierten Ausführungsbeispiel;
• 19 ist eine vergrößerte Querschnittsansicht eines Hauptteils des Kolbenkompressors gemäß dem vierten Ausführungsbeispiel entlang Linie D-D in 18; und
• 20 ist eine Seitenansicht eines ersten beweglichen Körpers eines Kolbenkompressors gemäß einem fünften Ausführungsbeispiel.

The disclosure, along with objects and advantages thereof, can be best understood by referring to the following description of the exemplary embodiments along with the accompanying drawings:

• 1 Fig. 3 is a cross-sectional view of a reciprocating compressor according to a first embodiment at a minimum flow rate;
• 2 Fig. 3 is a cross-sectional view of the reciprocating compressor according to the first embodiment at a maximum flow rate;
• 3 Fig. 13 is an exploded view of a drive shaft, movable body and the like of the reciprocating compressor according to the first embodiment;
• 4th Fig. 3 is a cross-sectional view of a lid of the reciprocating compressor according to the first embodiment;
• 5 FIG. 13 is an enlarged cross-sectional view of the lid of the reciprocating compressor according to the first embodiment along line CC in FIG 4th ;
• 6th Fig. 13 is an enlarged front view of a first movable body of the reciprocating compressor according to the first embodiment when the first movable body is viewed from the front side of the compressor;
• 7th Fig. 13 is an enlarged rear view of a second movable body of the reciprocating compressor according to the first embodiment when the second movable body is viewed from the rear side of the compressor;
• 8th Fig. 13 is an enlarged cross-sectional view of a main part of the reciprocating compressor according to the first embodiment at the minimum flow rate, the cross-sectional view showing the drive shaft, movable bodies and the like;
• 9 Fig. 13 is an enlarged cross-sectional view of a main part of the reciprocating compressor according to the first embodiment at the maximum flow rate, the cross-sectional view showing the drive shaft, movable bodies and the like;
• 10 FIG. 13 is an enlarged cross-sectional view of a main part of the reciprocating compressor according to the first embodiment along line AA in FIG 1 ;
• 11 FIG. 13 is an enlarged cross-sectional view of a main part of the reciprocating compressor according to the first embodiment, and illustrates a state in which the movable bodies move from the positions where the movable bodies in FIG 1 are shown, have moved further back, and is similar to 10 ;
• 12 FIG. 14 is an enlarged cross-sectional view of a main part of the reciprocating compressor according to the first embodiment along line BB in FIG 2 ;
• 13 Fig. 13 is a schematic drawing of the first movable body of the reciprocating compressor according to the first embodiment, and illustrates a positional relationship between the first movable body and a first communication passage at the minimum flow rate;
• 14th Fig. 13 is a schematic drawing of the first movable body of the reciprocating compressor according to the first embodiment, and illustrates a positional relationship between the first movable body and the first communication passage at an intermediate flow rate;
• 15th Fig. 13 is a schematic drawing of the first movable body of the reciprocating compressor according to the first embodiment, showing a positional relationship between the first movable body and the first communication passage at the maximum flow rate;
• 16 Fig. 13 is a side view of a first movable body of a reciprocating compressor according to a second embodiment;
• 17th Fig. 13 is a side view of a first movable body of a reciprocating compressor according to a third embodiment;
• 18th Fig. 13 is a side view of a first movable body of a reciprocating compressor according to a fourth embodiment;
• 19th FIG. 13 is an enlarged cross-sectional view of a main part of the reciprocating compressor according to the fourth embodiment along line DD in FIG 18th ; and
• 20th Fig. 13 is a side view of a first movable body of a reciprocating compressor according to a fifth embodiment.

DETAILED DESCRIPTION OF THE EMBODIMENTS

The following describes first to fifth embodiments of the present disclosure with reference to the accompanying drawings. The compressors described below are each a single head piston compressor. Each of the compressors can be mounted on a vehicle and included in a refrigeration cycle of an air conditioner.

First embodiment

As in 1 and 2 is shown, a compressor according to a first embodiment has a housing 1 , a drive shaft 3 , a fixed swash plate 5 , a variety of pistons 7th , a valve forming plate 9 , a movable body 10 and a control valve 13 . The valve-forming plate 9 is an example of the “dispensing valve” of the present disclosure.

The case 1 includes a front housing 17th , a rear case 19th and a cylinder block 21st . In the present embodiment, the front-rear direction of the compressor is by referring to the side on which the front housing 17th is positioned as the front side of the compressor and by reference to the side on which the rear housing 19th is positioned as defines the rear of the compressor. Furthermore, the up-down direction of the compressor is shown by referring to the top of FIG 1 and 2 as the top side of the compressor and by referring to the bottom side of 1 and 2 defined as the lower side of the compressor.

Furthermore, in 3 and the subsequent figures indicate the front-back direction and the top-bottom direction to correspond to those in 1 and 2 to correspond. The front-rear direction and the like in the embodiments are mere examples, and the compressor of the present disclosure can be appropriately mounted in various positions depending on the vehicle on which the compressor is mounted.

The front case 17th has a front wall 17a moving in a radial direction of the drive shaft 3 extends, and a peripheral wall 17b that are with the front wall 17a Is integrally formed and extends backwards from the front wall 17a in one direction of an axis O the drive shaft 3 extends. The front case 17th has a substantially cylindrical shape. The axis O the drive shaft 3 extends parallel to the front-rear direction of the compressor.

The front wall 17a has a first hub 171 , a second hub 172 and a first shaft hole 173 . The first hub 171 stands forward in one direction of the axis O the drive shaft 3 in front. A shaft sealing device 25th is in the first hub 171 arranged. The second hub 172 stands backwards in the direction of the axis O in a swash plate chamber 31 which will be described later. The first shaft hole 173 is through the front wall 17a in the direction of the axis O educated.

The rear case 19th has a suction chamber 28 , an inlet 28a , a delivery chamber 29 , an outlet 29a and a third connection passage 26c . The suction chamber 28 is approximately at a center of the rear case 19th located. The inlet 28a is with the suction chamber 28 in connection and extends in the rear housing 19th in an axial direction of the rear case 19th to get to an outside of the rear case 19th to open. The inlet 28a is connected to an evaporator by a pipe. Refrigerant gas at a low pressure, that is, refrigerant gas at a suction pressure, is introduced into the suction chamber 28 from the evaporator through the inlet 28a initiated through. As a result, a pressure in the suction chamber becomes 28 the suction pressure. The delivery chamber 29 is formed in an annular shape and is outside of the suction chamber 28 located. The outlet 29a is in connection with the delivery chamber 29 and extends in a radial direction of the rear housing 19th to get to the outside of the rear case 19th to open. The outlet 29a is connected by a line to a capacitor. The forms of inlet 28a and the outlet 29a can be determined appropriately. The line, the evaporator and the condenser are not shown in the drawings. The third connection pass 26c is with the suction chamber 28 connected at a position different from a position of the inlet 28a differs.

The cylinder block 21st is between the front case 17th and the rear case 19th located. As in 10 to 12 shown has the cylinder block 21st Cylinder bores 21a to 21f . The cylinder bores 21a to 21f are at equal angular intervals in a circumferential direction of the cylinder block 21st arranged. As in 1 and 2 As shown, each of the cylinder bores extends 21a to 21f in the direction of the axis O . The number of cylinder bores 21a to 21f can be determined appropriately.

The cylinder block 21st is on the front case 17th joined so that the swash plate chamber 31 between the front wall 17a and the perimeter wall 17b of the front housing 17th is trained. The swash plate chamber 31 is in connection with the suction chamber 28 via a passage (not shown).

The cylinder block 21st also has a second shaft hole 23 . The first shaft hole 173 and the second shaft hole 23 are examples of the “shaft hole” of the present disclosure. The second shaft hole 23 is about a center of the cylinder block 21st located and is through the cylinder block 21st through in the direction of the axis O educated. The cylinder block 21st is on the rear case 19th via the valve-forming plate 9 joined so that the rear portion of the second shaft hole 23 in the suction chamber 28 is located.

Accordingly, the second shaft hole is 23 in connection with the suction chamber 28 .

There is also an annular groove 24 in a front portion of the second shaft hole 23 educated. The annular groove 24 has an annular shape and is in an inner peripheral surface of the second shaft hole 23 recessed to on the inner peripheral surface of the second shaft hole 23 to open. The annular groove 24 is with a first connection passage 26a connected and is connected to a second connecting passage 26b connected at a position different from a position at which the annular groove 24 with the first pass 26a connected is. The first connection pass 26a and the second Connection passage 26b are in the cylinder block 21st and the rear case 19th educated. The first connection pass 26a is with the delivery chamber 29 at one end of the first connection pass 26a opposite to the other end of the first connecting passage 26a connected that with the annular groove 24 connected is. As a result, the first allows communication passage 26a a connection between the annular groove 24 and the delivery chamber 29 .

Furthermore, as in 10 to 12 shown is the cylinder block 21st a plurality of first connection passages 22a to 22f . The first connection passes 22a to 22f are between the cylinder bores 21a to 21f and the second shaft hole 23 located. The first connection passes 22a to 22f each connect the cylinder bores 21a to 21f with the second shaft hole 23 .

As in 1 and 2 is the valve forming plate 9 between the rear case 19th and the cylinder block 21st arranged. The rear case 19th and the cylinder block 21st are through the valve-forming plate 9 joined together.

The valve-forming plate 9 has a valve plate 90 , a dispensing valve plate 92 and a retaining plate 93 . The valve plate 90 has six dispensing holes 911 that with the cylinder bores 21a to 21f are connected. The cylinder bores 21a to 21f are about the dispensing holes 911 with the delivery chamber 29 connected.

The dispensing valve plate 92 is on a rear surface of the valve plate 90 arranged. The dispensing valve plate 92 has six dispensing diaphragm valves 92a that are elastically deformed to make the dispensing holes 911 to open and close. The retention plate 93 is on a rear surface of the discharge valve plate 92 arranged. The retention plate 93 defines a maximum degree of opening of the dispensing diaphragm valves 92a .

The drive shaft 3 has a drive shaft body 33 and a lid 35 and extends from the front of the housing 1 to the rear of the case 1 in the direction of the axis O . The drive shaft body 33 and the lid 35 are made of steel and have rigidity against a compressive load of a highly compressed refrigerant gas. The drive shaft body 33 forms a front portion of the drive shaft 3 out. The drive shaft body 33 has a threaded section 33a , a first shaft section 33b and a second shaft section 33c . The threaded section 33a is at a front end of the drive shaft body 33 located, that is, at a front end of the drive shaft 3 . The drive shaft 3 is connected to components (not shown), such as a pulley or an electromagnetic clutch, through the threaded portion 33a coupled. In this way the drive shaft gets 3 a driving force for rotation of the vehicle.

The first wave section 33b is adjacent to a rear end of the threaded portion 33a and extends in the direction of the axis O . The second wave section 33c is adjacent to a rear end of the first shaft section 33b and extends in the direction of the axis O . The second wave section 33c has a diameter that is smaller than a diameter of the first shaft section 33b . As in 3 is shown, the second shaft section 33c a first axial passage 33d . The first axial passage 33d extends in the direction of the axis O in the second shaft section 33c to on a rear end surface of the second shaft portion 33c to open, that is, at a rear end face of the drive shaft body 33 . The second wave section 33c has a first radial passage 33e . As in 9 and 10 is shown, the first radial passage extends 33e in the radial direction of the drive shaft 3 in the second shaft section 33c to on an outer peripheral surface of the second shaft portion 33c to open while having the first axial passage 33d is connected.

As in 1 and 2 is shown, forms the lid 35 a rear portion of the drive shaft 3 . As in 1 to 5 is shown has the lid 35 a cylindrical shape that is substantially the same diameter as a diameter of the second shaft hole 23 has, and extends in the direction of the axis O . As in 4th and 5 is shown has the lid 35 a guide window 35a . As in 5 is the guide window 35a over half the circumference of the lid 35 formed and extending in the direction of the axis O . Furthermore, part of the lid becomes 35 that is opposite to the guide window 35a with reference to the axis O is located as a main body 35b designated. The main body 35b has a semicircular gutter-like shape, is the guide window 35a facing and extending in the direction of the axis O . The lead window 35a can be larger than half the circumference of the lid 35 or can be smaller than half the circumference of the lid 35 .

As in 4th is shown is a second axial passage 35c in the lid 35 educated. The second axial passage 35c extends in the direction of the axis O and goes through the lid 35 in the front-back direction. The second axial passage 35c has a section 351 with a first diameter, a section 352 with a second diameter and a section 353 with a third diameter. The section 351 with the first diameter, the section 352 with the second diameter and the section 353 with the third diameter are coaxial with each other.

The section 351 with the first diameter has substantially the same diameter as the diameter of the second shaft section 33c of the drive shaft body 33 . The section 351 with the first diameter opens on a front end surface of the lid 35 and extends backwards. The section 352 the second diameter is with a rear end of the section 351 connected to the first diameter and extending rearward. The section 352 the second diameter has a diameter that is substantially the same as a diameter of the first axial passage 33d who is in 3 and is smaller than the diameter of the section 351 with the first diameter. Hence is a first stage 354 , in the 4th is shown between the section 351 with the first diameter and section 352 formed with the second diameter. The section 351 with the first diameter and the section 352 with the second diameter are in connection with the guide window 35a . The section 351 with the first diameter and the section 352 with the second diameter are with the outside of the lid 35 via the guide window 35a in connection. The section 353 with the third diameter is with a rear end of the section 352 connected to the second diameter and extending rearwardly to at a rear end surface of the lid 35 to open. The section with the third diameter 353 has a diameter smaller than the diameter of the section 352 with the second diameter. Hence there is a second stage 355 between the section 352 with the second diameter and section 353 formed with the third diameter.

There is also a first annular groove 356 and a second annular groove 357 in a front end portion of the lid 35 educated. A first sealing ring 358 is in the first annular groove 356 arranged, and a second sealing ring 359 is in the second annular groove 357 arranged. The first sealing ring 358 and the second sealing ring 359 are made of a resin material such as PTFE. Furthermore, in the front end portion of the lid 35 a second radial passage 35d between the first annular groove 356 and the second annular groove 357 formed, that is, between the first sealing ring 358 and the second sealing ring 359 . The second radial passage 35d is related to the section 351 having the first diameter and extending in the lid 35 in a radial direction of the lid 35 to on an outer peripheral surface of the lid 35 to open.

As in 3 to 5 is shown has the lid 35 a first boundary surface 301 , a second boundary surface 302 , a first end face 303 and a second end face 304 . As in 4th is shown, the first boundary surface extends 301 in a planar manner from an inner circumference to an outer circumference of the cover 35 and is oriented backwards to the guide window 35a to be facing. The second boundary surface 302 is the first boundary surface 301 facing, extends in a planar manner from the inner circumference to the outer circumference of the lid 35 and is oriented forward to the guide window 35a to be facing. As in 3 is the first end face 303 and the second end face 304 inside the guide window 35a located, that is, between the first boundary surface 301 and the second boundary surface 302 . The first end face 303 and the second end face 304 are arranged with the axis O between the first end face 303 and the second end face 304 is arranged, and extend in a planar manner parallel to each other in the direction of the axis O . Accordingly, the first end face 303 and the second end face 304 each with the first boundary surface 301 and the second boundary surface 302 connected. The first end face 303 and the second end face 304 form end faces of the main body 35b .

As in 8th and 9 is shown is the second shaft section 33c of the drive shaft body 33 on the lid 35 press fit. Specifically, is a rear end portion of the second shaft portion 33c on the section 351 with the first diameter of the second axial passage 35c press fit. A rear end of the second shaft section 33c is at the first stage 354 so that a position of the second shaft section 33c in the section 351 is determined with the first diameter. The first radial passage 33e and the second radial passage 35d fit together to be connected with each other. In this way is the drive shaft 3 formed as the drive shaft body 33 and the lid 35 are formed integrally with one another.

As in 1 and 2 is shown is the drive shaft 3 in the housing 1 rotatably used as the first shaft section 33b of the drive shaft body 33 and the lid 35 through the first shaft hole 173 or the second shaft hole 23 are supported. As a result, the drive shaft is 3 rotatable with respect to the axis O . In particular, the drive shaft rotates 3 in one direction R1 , in the 10 to 12 and so on.

The lid 35 is through the second shaft hole 23 supported so that the annular groove 24 the second radial passage 35d and the first radial passage 33e facing, as in 8th and 9 is shown. As a result, the annular groove 24 in connection with the first axial passage 33d over the first radial passage 33e and the second radial passage 35d . The first sealing ring also seals 358 and the second sealing ring 359 the gap between an interior of the second shaft hole 23 and the annular groove 24 from. The lid 35 is through the second shaft hole 23 supported so that the rear end of the lid 35 from the second shaft hole 23 into the suction chamber 28 protrudes. Accordingly, the second axial passage is 35c with the suction chamber 28 about the section 353 connected to the third diameter. As in 1 and 2 is shown is the drive shaft 3 into the shaft sealing device 25th used that in the first hub 171 is arranged. The shaft sealing device 25th seals the housing 1 from.

The lid 35 is through the second shaft hole 23 supported, and the guide window 35a and the main body 35b are the first connection passes 22a to 22f facing as in 10 to 12 is shown. In particular is the guide window 35a at least one of the first connection passages 22a to 22f facing that with its corresponding chamber of the compression chambers 45a to 45f is in connection in either a re-expansion stroke or an intake stroke. Furthermore is the main body 35b at least one of the first connection passages 22a to 22f facing that with a corresponding chamber of the compression chambers 45a to 45f is in communication in either a compression stroke or a discharge stroke. The compression chambers 45a to 45f will be explained later.

As in 1 and 2 shown is the fixed swashplate 5 on the second shaft section 33c of the drive shaft body 33 so press-fitted that the fixed swash plate 5 on the drive shaft body 33 is fixed. The fixed swashplate 5 is in contact with a stage 33f that is between the second shaft section 33c and the first shaft section 33b designed such that a position of the fixed swash plate 5 with respect to the drive shaft body 33 is determined. As a result, the swash plate is fixed 5 inside the swash plate chamber 31 arranged and is rotatable together with the drive shaft 3 in the swash plate chamber 31 by rotating the drive shaft 3 . The fixed swashplate 5 has a constant angle of inclination with respect to a plane perpendicular to the drive shaft 3 is. There is also a thrust bearing 6th between the second hub 172 and the fixed swashplate 5 in the swash plate chamber 31 arranged.

The pistons 7th are each in a different one of the cylinder bores 21a to 21f recorded. The pistons 7th act with the valve-forming plate 9 together to the compression chambers 45a to 45f in the respective cylinder bores 21a to 21f train as in 10 to 12 is shown. The compression chambers 45a to 45f are with the respective first connection passages 22a to 22f in connection. The valve-forming plate 9 is designed to take the refrigerant from the compression chambers 45a to 45f in the delivery chamber 29 submit.

As in 1 and 2 each of the pistons has 7th an engaging portion 7a . The engaging portion 7a takes hemispherical shoes 8a and 8b on. Each of the pistons 7th is with the fixed swashplate 5 through the shoes 8a and 8b coupled. The shoes 8a and 8b function as a converting mechanism for converting the rotation of the fixed swash plate 5 in a reciprocating motion of the piston 7th . As a result, the pistons move 7th each between a top dead center of the piston 7th and a bottom dead center of the piston 7th in a corresponding one of the cylinder bores 21a to 21f back and forth.

As in 3 shown has the movable body 10 a first movable body 11 and a second movable body 12 . As in 10 to 12 is shown is the movable body 10 on the drive shaft 3 attached so that the movable body 10 together with the drive shaft 3 with reference to the axis O turns. Accordingly, there are a front side and a rear side of the first movable body 11 in a direction of rotation of the first movable body 11 with the axis O defined between the front side and the rear side. The attachment of the movable body 10 on the drive shaft 3 will be explained later.

As in 6th and 10 to 12 shown has the first movable body 11 a peripheral wall portion 11a and a wall section 11b . The peripheral wall section 11a has a substantially semicircular groove-like shape and has substantially the same diameter as a diameter of the lid 35 and extends in the direction of the axis O . As in 8th and 9 is a length of the first movable body 11 in the direction of the axis O , that is, a length of the first movable body 11 in the front-back direction, shorter than a length of the guide window 35a in the front-back direction.

As in 6th has the peripheral wall portion 11a an outer surface 111 and an inner surface 112 . The peripheral wall section 11a has a second connection passage 41 . The second connection pass 41 is through a hole 41a passing through the peripheral wall section 11a is formed therethrough from the outer surface 111 to the inner surface 112 educated. As in 13 to 15th is shown, the second connecting passage extends 41 through the peripheral wall portion 11a in the front-back direction. With the extension of the second connecting passage 41 from the rear end to the front end thereof becomes the second communication passage 41 gradually longer in a circumferential direction of the peripheral wall portion 11a that is, from the front side to the rear side of the rotating direction of the first movable body 11 . The second connection pass 41 has a first region 411 and a second region 412 on a rear end side and a front end side of the second communication passage, respectively 41 are located. The second region 412 is larger than the first region 411 in the direction of rotation of the first movable body 11 .

The second connection pass 41 that is in the peripheral wall portion 11a is formed has such a shape that the second communication passage 41 a leading end edge 61 , a rear end margin 63 , a first connection edge 65 and a second connection edge 67 Has. The leading end edge 61 is on the foremost side in the rotating direction of the first movable body 11 located and extending in the direction of the axis O , that is, in the front-back direction of the first movable body 11 . The rear end edge 63 is on the rear side with respect to the front end edge 61 in the direction of rotation of the drive shaft 3 and the moving body 10 located and extending in the front-rear direction of the second communication passage 41 . With extension of the rear end margin 63 to the front side of the second communication passage 41 is the rear end margin 63 shaped to from the leading end edge 61 to be further away and towards the rear in the direction of rotation. The first connection edge 65 and the second connection edge 67 extend in a circumferential direction of the first movable body 11 and are each with the leading end edge 61 and the rear end margin 63 connected.

The leading end edge 61 has a first edge portion 61a , a second edge portion 61b and a third edge portion 61c . The first edge section 61a forms a leading end portion of the leading end edge 61 and is with the first connection edge 65 connected. The first edge section 61a is designed around the first connecting passages 22a to 22f to face when the flow rate of the refrigerant gas coming from the compression chambers 45a to 45f in the delivery chamber 29 is maximum, that is, at the maximum flow rate.

The third edge section 61c forms a rear end portion of the front end edge 61 and is with the second connection edge 67 connected. The third edge section 61c is designed around the first connecting passages 22a to 22f to face when the flow rate of the refrigerant gas coming from the compression chambers 45a to 45f in the delivery chamber 29 is at a minimum, i.e. at the minimum flow rate.

The second edge section 61b is between the first edge portion 61a and the third edge portion 61c located and is with the first edge portion 61a and with the third edge portion 61c connected. The second edge section 61b is designed around the first connecting passages 22a to 22f to face when the flow rate of the refrigerant gas coming from the compression chambers 45a to 45f in the delivery chamber 29 is less than the maximum flow rate and greater than the minimum flow rate (hereinafter “at the mean flow rate”). The mean flow rate corresponds to a certain range between the maximum flow rate and the minimum flow rate. Accordingly, the second edge portion extends 61b longer in the front-back direction than the first edge portion 61a and the third edge portion 61c . The facing relationship between the first, second, and third edge portions 61a to 61c and the first connection passages 22a to 22f at the maximum flow rate, the minimum flow rate and the mean flow rate will be explained later. Alternatively, the leading end edge 61 from a first edge section 61a and a second edge portion 61b exist when the second edge portion 61b is designed around the first connecting passages 22a to 22f facing at the minimum flow rate and at the intermediate flow rate.

The first edge section 61a is on the rear side relative to the second edge portion 61b and the third edge portion 61c in the direction of rotation of the drive shaft 3 and the moving body 10 located. The first edge section 61a has a curved region 611 leading to the second edge section 61b and is curved toward the front side in the rotating direction. The first edge section 61a is with the second edge portion 61b over the curved region 611 connected. That is, the first edge portion 61a is adjacent to the second edge portion 61b with gradual changes in the direction of rotation. As in 15th is shown has the curved region 611 a curvature that leads to the shapes of the first connecting passages 22a to 22f fits. In contrast, the second edge section 61b and the third edge portion 61c located at the same position in the direction of rotation.

As in 6th , 8th and 9 is the wall section 11b integral with the inner surface 112 of the peripheral wall portion 11a and is formed on a rear portion of the first movable body 11 arranged. The wall section 11b has a plate-like shape, extends in the up-down direction, and is perpendicular to the direction of the axis O . As in 6th shown has the wall section 11b an end face 113 . The end face 113 is on the opposite side from the peripheral wall portion 11a located. The wall section 11b also has a cutout 114 that has a semicircular shape. The shape of the cutout 114 can be determined as it is appropriate; however, the clipping is 114 not necessarily required. For ease of explanation are the wall section 11b and the neckline 114 in 13 to 15th not shown. The same applies 16 to 18th and 20th referred to later.

As in 3 and 7th to 9 shown has the second movable body 12 is substantially cylindrical in shape and has substantially the same diameter as the diameter of the first axial passage 33d and the diameter of the section 352 with the second diameter of the second axial passage 35c . An engaging section 12a in the shape of a flat plane is at a rear end of the second movable body 12 educated. The second movable body 12 has a connecting passage 120 .

As in 8th and 9 is shown, the connecting passage extends 120 in the direction of the axis O of the second movable body 12 to at the rear end of the second movable body 12 to open. The connecting passage 120 is also on the outer peripheral surface of the second movable body 12 at the engaging portion 12a open. The connecting passage 120 does not go through the second movable body 12 in the direction of the axis O through and therefore is not at a front end of the second movable body 12 open. As a result, the second has movable body 12 a first surface 121 and a second face 122 which are formed in the shape of flat planes. The first face 121 forms a front end surface of the second movable body 12 and is facing forward. The second face 122 is on the front side of the connecting passage 120 positioned and facing backwards. The shape of the engaging portion 12a can be determined as appropriate as long as engagement of the engaging portion 12a with the wall section 11b is permitted.

The second movable body 12 also has an annular groove 12b that between the first face 121 and the second surface 122 , that is, before the connection passage 120 , is trained. The ring groove 12b is with an O-ring 37 Mistake.

The second movable body 12 is in the section 352 with the second diameter of the lid 35 arranged, the engaging portion 12a the guide window 35a facing, that is, the connecting passage 120 the guide window 35a is facing. In the lid 35 is the front end of the second movable body 12 in the first axial passage 33d arranged. As a result, there is in the first axial passage 33d , that is, in the drive shaft 3 , a control pressure chamber 27 through the drive shaft body 33 and the second movable body 12 Are defined. The control pressure chamber 27 is with the annular groove 24 over the first radial passage 33e and the second radial passage 35d in connection. The first connection pass 26a who have favourited Annular Groove 24 , the first radial passage 33e and the second radial passage 35d work together to create a feed passage 13a to train. The delivery chamber 29 and the control pressure chamber 27 are through the feed passage 13a connected with each other. The O-ring 37 seals a gap between the control pressure chamber 27 and the section 352 with the second diameter.

Because the annular groove 24 in an annular shape in the second shaft hole 23 is recessed is the annular groove 24 the second radial passage 35d and the first radial passage 33e facing at all times, even while the drive shaft 3 turns. As a result, the annular groove 24 and the control pressure chamber 27 in communication with each other at all times, even while the drive shaft 3 turns.

The first movable body 11 is in the guide window 35a arranged, the wall section 11b the second movable body 12 is facing. The first movable body 11 is on the lid 35 attached, and the peripheral wall portion 11a is in the second shaft hole 23 opposite to the main body 35b with reference to the axis O located. Since the peripheral wall portion 11a has a semicircular channel-like shape and is substantially the same diameter as the diameter of the lid 35 , forms the first movable body 11 along with the main body 35b has a cylindrical body and has substantially the same diameter as the diameter of the second shaft hole 23 , with the first movable body 11 in the guide window 35a arranged as in 10 to 12 is shown. As a result, the first movable body fits 11 along with the main body 35b with the second shaft hole 23 together.

As in 8th and 9 is shown, touches the wall section 11b of the first movable body 11 the engaging portion 12a of the second movable body 12 , the first movable body 11 in the guide window 35a is arranged. The wall section 11b and the engaging portion 12a are engaged with each other so that the first movable body 11 and the second movable body 12 are assembled together. The moving body 10 is on the lid 35 appropriate. In other words, the body is movable 10 for the drive shaft and is in the second shaft hole 23 arranged. The second connection pass 41 is with the connecting passage 120 connected while making the connection passage 120 is facing.

The section 352 with the second diameter, the section 353 with the third diameter and the cutout 114 work together to create an intake passage 39 in the lid 35 , that is, in the drive shaft 3 to train. The connecting passage 120 is with the suction chamber 28 through the suction passage 39 connected. Accordingly, the suction passage 39 and the connecting passage 120 at the suction pressure. Furthermore, the connection passage allows 120 a connection of the second connection passage 41 with the suction chamber 28 via the suction passage 39 . The suction passage 39 is from the control pressure chamber 27 by the second movable body 12 Cut. Accordingly, the suction passage 39 and the connecting passage 120 not with the control pressure chamber 27 in connection.

The drive shaft rotates in this compressor 3 with reference to the axis O so that the rotation of the drive shaft 3 to the first movable body 11 over the first end face 303 is transmitted. As a result, the movable body is 10 who made the first movable body 11 has, rotatable together with the drive shaft 3 with reference to the axis O . Because the wall section 11b and the engaging portion 12a are engaged with each other is rotating the second movable body 12 with reference to the axis O regardless of the first movable body 11 in the first axial passage 33d and in the section 352 regulated with the second diameter.

It also acts in the lid 35 the suction pressure on the wall section 11b of the moving body 11 and the second face 122 of the second movable body 12 . In contrast, a control pressure acts on the first surface 121 of the second movable body 12 . The control pressure will be explained later.

Because the wall section 11b and the engaging portion 12a are engaged with each other is the first movable body 11 movable together with the second movable body 12 in the direction of the axis O . In other words, the body is movable 10 movable relative to the drive shaft 3 according to the control pressure (which will be explained later) in the direction of the axis O . Accordingly, the first movable body is 11 back and forth in the guide window 35a in the direction of the axis O movable. In contrast, the second is movable body 12 back and forth in the direction of the axis O movable by being in the first axial passage 33d and the section 352 with the small diameter slides. As a result, the movable body is 10 back and forth relative to the drive shaft 3 in the second shaft hole 23 in the direction of the axis O movable.

The second connection pass 41 is with interruptions with the first connection passes 22a to 22f by the rotation of the drive shaft 3 in connection, as in 10 to 12 is shown so that the refrigerant in the compression chambers 45a to 45f through the second connection passage 41 and the first connection passages 22a to 22f is initiated. Furthermore, the connection angle changes around the axis O passing through the second connection passage 41 and at least one of the first connection passages 22a to 22f is formed, which is formed with the second communication passage 41 is in connection, per rotation of the drive shaft 3 according to the position of the first movable body 11 in the guide window 35a . In the following description, the connection angle around the axis O around that through the second connecting passage 41 and at least one of the first connection passages 22a to 22f is formed, which is formed with the second communication passage 41 is in connection, per rotation of the drive shaft 3 simply referred to as a connecting bracket. Ask for an explanation for simplicity 4th to 9 the lid 35 , the first movable body 11 and the second movable body 12 in a state after the drive shaft 3 and the fixed swashplate 5 have rotated from the positions in 1 and 2 are shown. Furthermore, for ease of explanation, ask 8th to 12 the shape of the second connecting passage 41 and the like in a schematic manner.

As in 8th and 9 is shown is an urging spring 43 between the second stage 355 and the moving body 10 in the lid 35 intended. The urging spring 43 urges the moving body 10 to the front of the lid 35 .

As in 1 and 2 is the control valve 13 in the rear case 19th arranged. The control valve 13 is with the second connecting passage 26b connected. This allows the control valve to be connected 13 with the annular groove 24 and thus with the control pressure chamber 27 through the second connection passage 26b . The control valve 13 is also connected to the third connecting passage 26c connected. This allows the control valve to be connected 13 with the suction chamber 28 through the third connection passage 26c . In this way are the second connecting passage 26b and the third connection passage 26c through the control valve 13 connected with each other. As a result, the second communication passage works 26b and the third connection passage 26c together to create a drain passage 13b to train. That is, the control pressure chambers are in this compressor 27 and the suction chamber 28 through the drain passage 13b and the control valve 13 connected with each other. The control valve 13 is with the suction chamber 28 also connected by a detection passage (not shown).

In this compressor, part of the refrigerant gas flows in the discharge chamber 29 to the control pressure chamber 27 through the feed passage 13a . Furthermore, the refrigerant gas flows in the control pressure chamber 27 to the suction chamber 28 through the drain passage 13b . The control valve also records 13 the suction pressure in the suction chamber 28 through the detection passage and adjusts its valve opening degree so that the control valve 13 the degree of opening of the drain passage 13b adjusts to adjust the flow rate of the refrigerant gas passing through the discharge passage 13b flows. In particular, the control valve increases 13 , by increasing the valve opening degree, the flow rate of the refrigerant gas discharged from the control pressure chamber 27 through the drain passage 13b to the suction chamber 28 flows. In contrast, the control valve decreases 13 , by decreasing the valve opening degree, the flow rate of the refrigerant gas discharged from the control pressure chamber 27 through the drain passage 13b to the suction chamber 28 flows. In this way the control valve controls 13 the control pressure, which is the pressure of the refrigerant gas in the control pressure chamber 27 by changing the flow rate of the refrigerant gas flowing from the control pressure chamber 27 to the suction chamber 28 flows relative to the flow rate of the refrigerant gas discharged from the discharge chamber 29 to the control pressure chamber 27 flows. Alternatively, the third connection passage 26c with the swash plate chamber 31 instead of the suction chamber 28 so that the control valve 13 with the swash plate chamber 31 via the third connection passage 26c can be connected, in other words, the control pressure chamber 27 with the swash plate chamber 31 through the drain passage 13b and the control valve 13 get connected.

In the compressor configured as described above, the fixed swash plate rotates 5 in the swash plate chamber 31 by the rotation of the drive shaft 3 with reference to the axis O . As a result, the pistons move 7th each between the top dead center and the bottom dead center in the cylinder bores 21a to 21f back and forth. In the following description, the movement of each of the pistons 7th from top dead center to bottom dead center in its corresponding one of the cylinder bores 21a to 21f referred to as an advancement. In contrast, the movement of each of the pistons 7th from the bottom dead center to the top dead center in its corresponding one of the cylinder bores 21a to 21f referred to as a return movement. While the piston 7th The compression chambers are doing the advancement 45a to 45f in the re-expansion stroke in which the refrigerant gas that remains in the compression chambers (hereinafter “remaining gas”) re-expands. Then are the first connection passes 22a to 22f with the second connection passage 41 in communication so that the process proceeds to the suction stroke in which the refrigerant gas is introduced. In contrast, while the pistons are 7th make the return movement, the compression chambers 45a to 45f in the compression stroke in which the refrigerant gas in the compression chambers 45a to 45f is compressed. The process then continues to the delivery stroke, in which the compressed refrigerant gas enters the delivery chamber 29 is delivered. While the piston 7th making the return movement is a connection of the first connection passages 22a to 22f and the second connection passage 41 not allowed with each other. Furthermore, the refrigerant gas that is in the discharge stroke in the discharge chamber 29 is dispensed through the outlet 29a delivered to the capacitor.

In particular, make this compressor while the drive shaft 3 at the angle of rotation given in 1 , 2 and 10 to 12 is shown the piston 7th the advancement in the compression chambers 45a to 45c . In other words, it is the piston 7th in the compression chamber 45a at an early stage of advancement, while the piston 7th in the compression chamber 45b at a middle stage of the Advancement is further ahead than the early stage and the piston 7th in the compression chamber 45c is at a later stage of advancement, which is further ahead than the middle stage. In contrast, do in the compression chambers 45d to 45f the corresponding pistons 7th the return movement. In other words, it is the piston 7th in the compression chamber 45d at an early stage of the return movement, which corresponds to an early stage of the compression stroke. The piston 7th in the compression chamber 45e is at an intermediate stage of the return movement, which corresponds to an intermediate stage of the compression stroke. The moreover one is the piston 7th in the compression chamber 45f at a later stage of the return movement, which corresponds to the transition from a later stage of the compression stroke to the discharge stroke. In 10 to 12 are, for simplicity of explanation, the pistons 7th not shown.

Furthermore, the compressor has the first movable body 11 in the guide window 35a arranged so that the first movable body 11 at least one of the first connection passages 22a to 22f facing that with the corresponding one of the compression chambers 45a to 45f is in connection with the corresponding piston 7th makes the movement. In particular, the first is movable body 11 while the drive shaft 3 at the angle of rotation given in 1 , 2 and 10 to 12 is shown, the first connection pass 22a that with the compression chamber 45a is in connection, the first connection passage 22b that with the compression chamber 45b is in communication, and the first connection passage 22c facing that with the compression chamber 45c is connected. Then when the drive shaft 3 in that direction R1 from the state in 10 and so on is shown, keeps turning, the piston makes 7th in the compression chamber 45f the advancement while the piston 7th in the compression chamber 45c makes the return movement. Accordingly, the first movable body is 11 the first connection pass 22f that with the compression chamber 45f is in connection, the first connection passage 22a that with the compression chamber 45a is in communication, and the first connection passage 22b facing that with the compression chamber 45b is connected. In this way is the first movable body 11 by the rotation of the drive shaft 3 , in a sequential manner certain passes from the first connection passes 22a to 22f facing that with the corresponding chambers of the compression chambers 45a to 45f are in connection in which the corresponding pistons 7th make the advance.

As a result, the at least one of the compression chambers goes 45a to 45f in which the corresponding piston 7th makes the forward movement, from the re-expansion stroke to the intake stroke. As a result, the refrigerant gas becomes in the suction chamber 28 into the at least one of the compression chambers 45a to 45f in the suction stroke through the suction passage 39 , the connection passage 120 , the second connection pass 41 and the corresponding one of the first connection passages 22a to 22f initiated. In other words, the first is movable body 11 sequentially certain passes from the first connection passes 22a to 22f facing that with the corresponding chambers of the compression chambers 45a to 45f that are in either the re-expansion stroke or the intake stroke.

The main body 35b of the lid 35 is on the opposite side from the guide window 35a located, that is, on the opposite side from the first movable body 11 with reference to the axis O . Because of this, the main body is 35b at least one of the first connection passages 22a to 22f , the one with the corresponding one of the compression chambers 45a to 45f is in communication in which the corresponding piston 7th the return movement makes, facing. Specifically is the main body 35b while the drive shaft 3 at the angle of rotation given in 1 , 2 and 10 to 12 is shown, the first connection pass 22d that is in communication with the compression chamber 45d is, the first connection pass 22e that is in communication with the compression chamber 45e and the first connection pass 22f that is in communication with the compression chamber 45f is facing. In this way is the main body 35b by the rotation of the drive shaft 3 , in a sequential manner certain passes from the first connection passes 22a to 22f facing that with the corresponding chambers of the compression chambers 45a to 45f are in connection in which the corresponding pistons 7th make the advance movement, i.e. the passages of the first connecting passages 22a to 22f that correspond to the corresponding chambers of the compression chambers 45a to 45f that are in either the compression stroke or the discharge stroke.

In addition, the movable body moves in the compressor 10 relative to the drive shaft 3 in the direction of the axis O so that it is possible to change the flow rate of the refrigerant gas flowing from the suction chamber 28 into the compression chambers 45a to 45f per rotation of the drive shaft 3 is initiated. As a result, in the compressor, it is possible to change the flow rate of the refrigerant gas flowing from the Compression chambers 45a to 45f in the delivery chamber 29 is delivered.

Specifically, to decrease the flow rate of the refrigerant gas from the compression chambers 45a to 45f in the delivery chamber 29 is dispensed, the control valve increases 13 its valve opening degree to the opening degree of the exhaust passage 13b to increase, thereby increasing the flow rate of the refrigerant gas discharged from the control pressure chamber 27 to the suction chamber 28 flows. In this way the control valve decreases 13 the control pressure in the control pressure chamber 27 . As a result, a variable differential pressure that is the differential pressure between the control pressure and the suction pressure decreases.

As a result, begins in the movable body 10 , the second movable body 12 from the position in 9 is shown within the first axial passage 33d and the section 352 with the second diameter in the direction of the axis O move forward due to the urging force of the urging spring 43 . The first movable body 11 also begins to look in the guide window 35a in the direction of the axis O due to the urging force of the urging spring 43 to move forward. As a result, the second communication passage moves 41 forward relative to the first connecting passages 22a to 22f . As a result, in the compressor, the connection angle gradually decreases.

As the control valve 13 the control pressure in the control pressure chamber 27 further reduced, the variable differential pressure reaches a minimum. As a result, as in 8th is shown in the movable body 10 the first movable body 11 to the foremost position in the guide window 35a and touches the first boundary surface 301 . This regulates the forward movement of the first movable body 11 in the guide window 35a . This further regulates the forward movement of the second movable body 12 in the first axial passage 33d and the section 352 with the second diameter over the first movable body 11 . This is how the first movable body moves 11 to the foremost position in the guide window 35a so that the second connecting passage 41 with the first connection passes 22a to 22f at the first region 411 is connected. As a result, the connection angle in the compressor reaches a minimum angle.

When the drive shaft 3 at the angle of rotation given in 10 is the first pass through 22a with the second connection passage 41 through the first movable body 11 connected. Furthermore, the first connection passages are 22b , 22c from the second connection passage 41 through the peripheral wall portion 11a of the first movable body 11 Cut. That is, only one pass of the first connection passes 22a to 22f , the one with the corresponding chamber of the compression chambers 45a to 45f is in connection with the corresponding piston 7th is at the early stage of advancement is through the first moving body 11 with the second connection passage 41 connected. In contrast, the first are connecting passes 22d to 22f from the second connection passage 41 through the main body 35b of the lid 35 the drive shaft 3 Cut. Accordingly, at least one of the first connecting passages is 22a to 22f , the one with the corresponding chamber of the compression chambers 45a to 45f which is in either the compression stroke or the discharge stroke, through the main body 35b from the second connection passage 41 Cut.

The explanation continues while the compression chamber 45a and the first connection passage 22a that with the compression chamber 45a can be used as examples. When the variable differential pressure is at the minimum and therefore the connection angle is at the minimum, the first movable body is 11 at the foremost position in the guide window 35a located as in 13 and in the second connecting passage 41 is the third edge section 61c of the leading edge 61 the first connection pass 22a facing. Furthermore, as the first movable body 11 together with the drive shaft 3 rotates, the first connecting passage moves 22a to the rear side in the rotating direction relative to the third edge portion 61c that is, it makes a relative movement from the bottom to the top of 13 . The first connection pass 22a is in communication with the second connecting passage 41 until the first connection pass 22a the rear end margin 63 is facing. As a result, the compression chamber goes 45a from the re-expansion stroke to the intake stroke. Furthermore is the first connection passage 22a the rear end margin 63 facing so that the suction stroke ends.

As explained above, as a result of the connection angle reaching the minimum angle only during the piston 7th is at the early stage of advancement, the refrigerant gas is from the suction chamber 28 into the corresponding chamber of the compression chambers 45a to 45f through the suction passage 39 , the connection passage 120 , the second connection pass 41 and the corresponding one of the first connection passages 22a to 22f initiated. As a result, the flow rate of the refrigerant gas reaches that of the suction chamber 28 into the compression chambers 45a to 45f is initiated, the minimum. In this way, the compressor reduces the refrigerant gas flowing from the compression chambers 45a to 45f in the delivery chamber 29 is discharged to the minimum flow rate.

In order to increase the flow rate of the refrigerant gas coming from the compression chambers 45a to 45f in the delivery chamber 29 is released, the control valve decreases 13 its valve opening degree to the opening degree of the exhaust passage 13b to decrease, thereby reducing the flow rate of the refrigerant gas discharged from the control pressure chamber 27 to the suction chamber 28 flows. In this way the control valve increases 13 the control pressure in the control pressure chamber 27 . As a result, the variable differential pressure becomes higher than the minimum pressure.

As a result, begins in the movable body 10 , the second movable body 12 a backward movement from the position in 8th is shown in the first axial passage 33d and the section 352 with the second diameter in the direction of the axis O against the urging force of the urging spring 43 . The first movable body 11 a rearward movement also begins in the guide window 35a in the direction of the axis O against the urging force of the urging spring 43 . As a result, the second communication passage moves 41 rearward relative to the first connecting passages 22a to 22f . Therefore, in the compressor, the connection angle becomes larger than the minimum angle and smaller than the maximum angle.

As a result, when the drive shaft 3 at the angle of rotation given in 11 are the first passages 22a and 22b through the first movable body 11 with the second connection passage 41 connected. Furthermore is the first connection passage 22c from the second connection passage 41 through the peripheral wall portion 11a of the first movable body 11 Cut. In other words, are one of the first connecting passages 22a to 22f , the one with the corresponding chamber of the compression chambers 45a to 45f is in connection with the corresponding piston 7th is at the early stage of advancement, and one of the first passages of communication 22a to 22f , the one with the corresponding chamber of the compression chambers 45a to 45f is in connection with the corresponding piston 7th is at the middle stage of advancement, by the first moving body 11 with the second connection passage 41 connected. In this situation there is the first connection passes 22d to 22f from the second connection passage 41 are separated, at least one of the first connection passages 22a to 22f , the one with the corresponding chamber of the compression chambers 45a to 45f that is in either the compression stroke or the discharge stroke from the second communication passage 41 Cut.

The explanation continues while the compression chamber 45a and the first connection passage 22a can be used as examples. When the variable differential pressure becomes higher than the minimum pressure, the first movable body moves 11 backwards in the guide window 35a as with the fat arrow in 14th and, in the second connecting passage 41 , is the second edge section 61b of the leading edge 61 the first connection pass 22a facing. Furthermore, the first communication passage moves 22a when the first moving body 11 together with the drive shaft 3 rotates, to the rear side in the rotating direction relative to the second edge portion 61b . Hence, the first connection pass is 22a in connection with the second connection passage 41 until the first connection pass 22a the rear end margin 63 is facing. In this situation when the second edge portion 61b the first connection pass 22a is facing, is the rear end edge 63 located further to the rear side in the rotating direction compared to when the third edge portion 61c the first connection pass 22a is facing. As a result, if the second edge portion 61b the first connection pass 22a facing, the connection angle is greater than the minimum angle.

As a result of the connection angle becoming larger than the minimum angle as described above while the piston is moving 7th is in the course of the early stage to the middle stage of advancement, the refrigerant gas is from the suction chamber 28 into the corresponding chamber of the compression chambers 45a to 45f through the suction passage 39 , the connection passage 120 , the second connection pass 41 and the corresponding one of the first connection passages 22a to 22f initiated. As a result, the flow rate of the refrigerant gas flowing from the suction chamber 28 into the compression chambers 45a to 45f is introduced, greater than the minimum flow rate. As a result, in the compressor, the flow rate of the refrigerant gas reaches that of the compression chambers 45a to 45f in the delivery chamber 29 is the mean flow rate. In this situation, as in 13 and 14th is shown, the second edge portion 61b and the third edge portion 61c located at the same position in the direction of rotation. Accordingly, the point in time when the compression chambers 45a to 45f from the re- The expansion stroke goes over to the suction stroke, in other words the positions of the pistons are the same 7th that do the advancement are the same at the minimum flow rate and the mean flow rate.

The control valve 13 further increases the control pressure in the control pressure chamber 27 so that the variable differential pressure reaches a maximum pressure. As in 8th shown moves in the movable body 10 , the first movable body 11 to the rearmost position in the guide window 35a and touches the second boundary surface 302 . This regulates the movement of the first movable body 11 backwards in the guide window 35a . This further regulates the movement of the second movable body 12 rearward in the first axial passage 33d and the section 352 with the second diameter. This is how the first movable body moves 11 to the rearmost position in the guide window 35a so that the second connecting passage 41 with the first connection passes 22a to 22f in the second region 412 is connected. As a result, in the compressor, the connection angle reaches a maximum angle.

As a result, if the drive shaft 3 at the angle of rotation given in 12 is shown, the first connection passages 22a to 22c with the second connection passage 41 through the first movable body 11 connected. In other words, passages are the first connection passages 22a to 22f that correspond to the corresponding chambers of the compression chambers 45a to 45f are in connection in which the corresponding pistons 7th are at the early stage, the middle stage, or the later stage of advancement, by the first movable body 11 with the second connection passage 41 connected. In this situation, the first connection passes are 22d to 22f from the second connection passage 41 through the first movable body 11 separate, in other words are the first connecting passages 22a to 22f that correspond to the corresponding chambers of the compression chambers 45a to 45f that are in either the compression stroke or the discharge stroke from the second communication passage 41 through the first movable body 11 Cut.

The explanation continues while the compression chamber 45a and the first connection passage 22a that with the compression chamber 45a can be used as examples. When the variable differential pressure reaches the maximum, the first moving body has moved 11 to the rearmost position in the guide window 35a moves as with the bold arrow in 15th and in the second connecting passage 41 is the first edge section 61a of the leading edge 61 the first connection pass 22a facing. It also moves by rotating the first movable body 11 together with the drive shaft 3 , the first connection pass 22a to the rear side in the rotating direction relative to the first edge portion 61a . Hence, the first connection pass is 22a in connection with the second connection passage 41 until the first connection pass 22a the rear end margin 63 is facing. In this situation is when the first edge section 61a the first connection pass 22a facing, the rear end edge 63 located further to the rear side in the rotating direction compared to when the second edge portion 61b or the third edge portion 61c the first connection pass 22a is facing. As a result, the connection angle reaches when the first edge portion 61a the first connection pass 22a is facing the maximum.

As explained above, when the connection angle is at the maximum, the refrigerant gas is from the suction chamber 28 in at least one chamber of the compression chambers 45a to 45f while the corresponding piston 7th is in the course of the early stage to the later stage of advancement, through the suction passage 39 , the connection passage 120 , the second connection pass 41 and the corresponding one of the first connection passages 22a to 22f initiated. As a result, the flow rate of the refrigerant gas reaches that of the suction chamber 28 into the compression chambers 45a to 45f is initiated, the maximum flow rate. In this way, the compressor increases the flow rate of a refrigerant gas flowing from the compression chambers 45a to 45f in the delivery chamber 29 is delivered to the maximum flow rate.

In this situation is the first edge portion 61a further on the rear side in the rotating direction compared to the second edge portion 61b and the third edge portion 61c located. To explain this, during the first connection pass 22a used as an example, at the maximum flow rate, is the first communication passage 22a the first edge section 61a not facing when the drive shaft 3 at such an angle of rotation through which the second Connection passage 41 a connection with the first connection passage 22a would start at the minimum flow rate and the intermediate flow rate, and the second connecting passage 41 is therefore from the first pass through 22a Cut. In other words, the drive shaft must 3 , at the maximum flow rate, in the direction R1 rotate further compared to the angle of rotation of the drive shaft 3 through which the second connection passage 41 a connection with the first connection passage 22a would start at the minimum flow rate and the mean flow rate. As a result, at the maximum flow rate, the point in time is the compression chambers 45a to 45f pass from the re-expansion stroke to the suction stroke, later than the time at which the compression chambers 45a to 45f transition from the re-expansion stroke to the suction stroke at the minimum flow rate and the mean flow rate. In other words, at the maximum flow rate, the compression chambers go 45a to 45f from the re-expansion stroke to the intake stroke at the point in time when the piston 7th has moved further in advance compared to the situations at the minimum flow rate and the mean flow rate. So to speak it is at the maximum flow rate because of the compression chambers 45a to 45f pass from the re-expansion stroke to the intake stroke when the piston 7th closer to an intermediate stage of advancement is the amount of time the re-expansion stroke takes per rotation of the drive shaft 3 longer, and the suction stroke therefore starts later than the re-expansion stroke and the suction stroke at the minimum flow rate and the intermediate flow rate. It should be noted that, at the maximum flow rate, the suction stroke starts later than explained herein, but the flow rate of the refrigerant gas reaches that of the suction chamber 28 into the compression chambers 45a to 45f is introduced, the maximum because the refrigerant gas from the suction chamber 28 is initiated even while the piston 7th is at the later stage of advancement, as explained above.

In this compressor is the pressure of the refrigerant gas coming from the compression chambers 45a to 45f in the delivery chamber 29 at the maximum flow rate is higher than the pressure of the refrigerant gas at the minimum flow rate and the intermediate flow rate. Thus, at the maximum flow rate, the pressure of the remaining gas that is in the discharge stroke is not into the discharge chamber 29 has been released and in the compression chambers 45a to 45f remains even higher than the pressure of the refrigerant gas at the minimum flow rate and the intermediate flow rate.

In this regard, this compressor is because of the time when the first connection passes 22a to 22f with the second connection passage 41 at the maximum flow rate are in communication later than that observed at the minimum flow rate and the mean flow rate, the time at which the compression chambers are in communication 45a to 45f transition from the re-expansion stroke to the suction stroke later than that observed at the minimum flow rate and the mean flow rate. As a result, the compressor sufficiently reduces the pressure of the remaining gas in the re-expansion stroke at the maximum flow rate. As a result, when the first connection passes 22a to 22f with the second connection passage 41 are in communication, i.e. at the beginning of the suction stroke, it is possible to prevent the remaining gas in the compression chambers from flowing back 45a to 45f into the second connection passage 41 and thus into the suction chamber 28 to restrict. As a result, it is unlikely to occur even during the first few connection passes 22a to 22f with the second connection passage 41 the pressure in each of the compression chambers 45a to 45f drops sharply. In this way the pistons can 7th as they move from the top dead center to the bottom dead center, the pressure in the compression chambers 45a to 45f during the re-expansion stroke, that is, use the pressure of the remaining gas in a suitable manner. Every piston moves in this compressor 7th easily from the top dead center to the bottom dead center at the maximum flow rate, so that it is possible to increase the driving force for the rotation of the drive shaft 3 to avoid. Furthermore, the remaining gas in the compression chambers will flow back 45a to 45f remains in the second connection passage 41 limited so that the compressor stops the suction pulsation at the maximum flow rate.

In contrast, at the minimum flow rate and the intermediate flow rate, the pressure of the refrigerant gas flowing from the compression chambers is 45a to 45f in the delivery chamber 29 is released, lower, and so does the pressure of the remaining gas that is in the compression chambers 45a to 45f remains is therefore lower than those pressures at the maximum flow rate. In this regard, this compressor is the time when the first connection passes 22a to 22f with the second connection passage 41 at the minimum flow rate and the mean flow rate are related earlier than the time point observed at the maximum flow rate. Accordingly, the point in time when the compression chambers 45a to 45f transition from the re-expansion stroke to the intake stroke earlier than that observed at the maximum flow rate.

As a result, this compressor prevents, at the minimum flow rate and the intermediate flow rate, the pressure inside the compression chambers 45a to 45f becomes lower than the suction pressure, that is, the pressure in the suction chamber 28 , through the re-expansion stroke. Hence, because each piston 7th is easily moved from the top dead center to the bottom dead center even at the minimum flow rate and the intermediate flow rate, it is possible to increase the driving force for the rotation of the drive shaft 3 to avoid. Furthermore, because it prevents the pressure inside the compression chambers 45a to 45f becomes lower than the suction pressure, this compressor suppresses the suction pulsation at the minimum flow rate and the intermediate flow rate.

Accordingly, according to the compressor of the first embodiment, it is possible to increase the driving force for rotation of the drive shaft 3 during the operation of the compressor, and it is also possible to prevent the suction pulsation.

Furthermore, in this compressor, part of the high pressure refrigerant gas that has been compressed in the compression stroke flows to the inside of the second shaft hole 23 through at least one of the first connection passages 22a to 22f , the one with the corresponding chamber of the compression chambers 45a to 45f which is in either the compression stroke or the discharge stroke. In this regard, the movable body has 10 this compressor was the first moving body 11 and the second movable body 12 while the lid 35 the guide window 35a has in which the first movable body 11 is arranged to be in the direction of the axis O to be agile. In this compressor with these arrangements is in the second shaft hole 23 , the main body 35b of the lid 35 at least one of the first connection passages 22a to 22f facing that with the corresponding chamber of the compression chambers 45a to 45f which is in either the compression stroke or the discharge stroke. In this way, at least one of the first connection passages is 22a to 22f , the one with the corresponding chamber of the compression chambers 45a to 45f which is in either the compression stroke or the discharge stroke, through the main body 35b from the second connection passage 41 Cut. In this situation it takes because of the lid 35 The lid is made of steel 35 , that is, the drive shaft 3 in the compressor, the compression load from the compression chambers 45a to 45f that are in either the compression stroke or the discharge stroke as appropriate.

As a result, because it is more difficult for the compressive load on the first moving body 11 and thus on the moving body 10 to act, the moving body moves 10 slightly in the direction of the axis O . As a result, the compressor easily changes the flow rate of the refrigerant gas flowing from the compression chambers 45a to 45f in the delivery chamber 29 per rotation of the drive shaft 3 is delivered. Furthermore, in the compressor, it is not necessary to have the second movable body 12 to be excessively large for the purpose of enlarging the pressure receiving area for the control pressure. As a result, it is also possible to keep the compressor compact.

Also in the compressor is on the leading end edge 61 of the second connection passage 41 , the first edge section 61a with the second edge portion 61b over the curved region 611 connected. Accordingly, the first edge portion is 61a adjacent to the second edge portion 61b with the gradual changes in the direction of rotation. As a result, it is possible to have the degree of freedom in designing the second communication passage 41 as well as the front end edge 61 is kept high to appropriately set the time when the first connection passes 22a to 22f with the second connection passage 41 are in communication at the maximum flow rate, and appropriately set the timing at which the first communication passages 22a to 22f with the second connection passage 41 are related at the times of the minimum flow rate and the mean flow rate.

Further, in the compressor, in the transition period that changes from the average flow rate to the maximum flow rate, the timing when the first communication passages becomes 22a to 22f with the second connection passage 41 are connected by the presence of the curved region 611 gradually later. Furthermore, because the curved region 611 is formed to have the curve leading to the first connection passages 22a to 22f fits is the curved region 611 suitably the first connection passages 22a to 22f facing. As a result, it is possible to appropriately prevent the refrigerant gas from flowing from the second communication passage 41 in the first connection passes 22a to 22f through the curved region 611 escapes, that is, in a suitable manner to prevent the time when the first connection passes 22a to 22f with the second connection passage 41 are connected at the curved region 611 earlier will.

Furthermore, the compressor performs outlet-side control by which the flow rate of the refrigerant gas discharged from the control pressure chamber 27 to the suction chamber 28 through the drain passage 13b flows through the control valve 13 will be changed. With this Arrangement, the compressor reduces the volume of the refrigerant gas in the discharge chamber 29 to be used to change the flow rate of the refrigerant gas flowing from the compression chambers 45a to 45f in the delivery chamber 29 is delivered. As a result, it is possible to increase the efficiency of the compressor.

Second embodiment

As in 16 are shown in a compressor according to a second embodiment, at the leading end edge 61 of the second connection passage 41 , the first edge section 61a , the second edge section 61b and the third edge portion 61c adjacent to each other with gradual changes in the direction of rotation. As a result, the leading end edge extends 61 , from the rear end to the front end of itself, gradually from the front side to the rear side of the direction of rotation. The other configurations of the compressor are the same as those of the compressor according to the first embodiment. The same configurations are referred to by using the same reference numerals, and the detailed explanations of these configurations are omitted.

In this compressor, while the flow rate changes from the minimum flow rate to the intermediate flow rate and to the maximum flow rate, the timing at which the first communication passages are changed changes 22a to 22f with the second connection passage 41 connected to be gradually later. In this way, the compressor can also achieve the same advantageous effects as those of the compressor according to the first embodiment.

Third embodiment

As in 17th is shown has, in a compressor according to a third embodiment, at the leading end edge 61 of the second connection passage 41 , the first edge section 61a a step 612 and is adjacent to the second edge portion 61b with the level 612 . With this arrangement, the leading end edge changes in the compressor 61 once from the second edge portion 61b to the first edge portion 61a at the stage 612 . The other configurations of the compressor are the same as those of the compressor according to the first embodiment.

In the compressor, when the flow rate changes from the middle flow rate to the maximum flow rate, the timing at which the first communication passages are made changes 22a to 22f with the second connection passage 41 are connected because of the stage 612 drastic. In other words, in the compressor, when the flow rate changes from the intermediate flow rate to the maximum flow rate, the timing at which the first communication passages are changed changes 22a to 22f with the second connection passage 41 connected to be sometime later. The other advantageous effects of the compressor are the same as those of the compressor according to the first embodiment.

Fourth embodiment

As in 18th and 19th is shown, in a compressor according to a fourth embodiment, the second connection passage 41 through the hole 41a and a recess 41b educated. The recess 41b is in the outer surface 111 left out. The recess 41b is with the hole 41a in connection while they are the hole 41a is facing. Accordingly, in the compressor is the leading end edge 61 of the second connection passage 41 through the hole 41a and the recess 41b educated. Specifically are on the leading end edge 61 the second edge portion 61b and the third edge portion 61c through the recess 41b educated. Accordingly, the second edge portion 61b and the third edge portion 61c on the front side in the direction of rotation of the first movable body 11 relative to the first edge portion 61a located. Furthermore, in the compressor, the first edge portion has 61a the stage 612 and is adjacent to the second edge portion 61b , that is, the recess 41b . The other configurations of the compressor are the same as those of the compressor according to the first embodiment.

In the compressor, at the medium flow rate, is the second edge portion 61b of the leading edge 61 the first connection passes 22a to 22f facing. Furthermore, the first movable body rotates 11 together with the drive shaft 3 so that the first connection passes 22a to 22f to the rear side of the rotating direction relative to the second edge portion 61b move and the recess 41b are facing. As a result, it flows during the first connecting passages 22a to 22f the recess 41b face the refrigerant gas in the first communication passages 22a to 22f from the hole 41a through the recess 41b through. The same applies to the minimum flow rate. Accordingly, in the compressor, at the minimum flow rate and the intermediate flow rate, there is the timing when the first communication passages 22a to 22f with the second connection passage 41 are in communication earlier than that observed at the maximum flow rate. In other words, in the compressor where maximum flow rate, the time at which the first connection passes 22a to 22f with the second connection passage 41 are in connection later than that observed at the minimum flow rate and the mean flow rate. The other advantageous effects of the compressor are the same as those of the compressor according to the first embodiment.

Fifth embodiment

As in 20th is shown in a compressor according to a fifth embodiment, at the leading end edge 61 of the second connection passage 41 , the third margin section 61c on the rear side in the direction of rotation of the first movable body 11 relative to the second edge portion 61b located. Specifically is the third edge portion 61c on the rear side of the direction of rotation relative to the second edge portion 61b and on the front side of the rotating direction relative to the first edge portion 61a located. In other words, at the leading end edge 61 , the second edge section 61b located farthest on the front side in the direction of rotation. Furthermore, the first edge section has 61a the stage 612 and is adjacent to the second edge portion 61b with the level 612 . Furthermore, the third edge section has 61c a step 613 and is adjacent to the second edge portion 61b with the level 613 . As a result, the leading end edge changes in the compressor 61 from the second edge portion 61b to the first edge portion 61a once at the step 612 , and continues to change from the third edge portion 61c to the second edge portion 61b once at the step 613 . The other configurations of the compressor are the same as those of the compressor according to the first embodiment.

In the compressor is the third edge portion 61c on the rear side of the direction of rotation relative to the second edge portion 61b located. At the minimum flow rate is the time when the first connecting passages 22a to 22f with the second connection passage 41 are in connection later than that observed at the mean flow rate. As a result, in the compressor there is the point of time when the compression chambers 45a to 45f transition from the re-expansion stroke to the suction stroke at the minimum flow rate, later than that observed in the compressor according to the first embodiment. As a result, in the compressor, the suction stroke time is even shorter at the minimum flow rate, so that the flow rate of the refrigerant gas flowing into the compression chambers 45a to 45f is introduced is smaller, and therefore the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f in the delivery chamber 29 is given, smaller. In this situation because of the third edge section 61c on the front side in the direction of rotation relative to the first edge portion 61a is the point in time at which the first connection passes 22a to 22f with the second connection passage 41 are connected at the minimum flow rate, earlier than the time at which the first connecting passages 22a to 22f with the second connection passage 41 are in communication at the maximum flow rate. The other advantageous effects of the compressor are the same as those of the compressor according to the first embodiment.

Alternatively, the position of the third edge portion in the compressor 61c be designed in the direction of rotation so that the time at which the first connection passages 22a to 22f with the second connection passage 41 at the minimum flow rate are in communication is equal to the time at which the first communication passages 22a to 22f with the second connection passage 41 are in communication at the maximum flow rate. As yet another example, the position of the third edge portion 61c be designed in the direction of rotation so that the time at which the first connection passages 22a to 22f with the second connection passage 41 communicating at the minimum flow rate is later than the time at which the first communication passages 22a to 22f with the second connection passage 41 are in communication at the maximum flow rate.

The present disclosure has thus been explained as the first to fifth embodiments; however, the present disclosure is not limited to the first to fifth embodiments. Needless to say, it is possible to carry out the present disclosure with certain modifications as appropriate without departing from the gist thereof.

For example, the compressor according to one of the first to fifth embodiments can be configured as a compressor with a double-headed piston.

Furthermore, in the compressor according to any one of the first to fifth embodiments, a projection or the like may be provided to move toward the rear side of the rotating direction of the first movable body 11 protrude at the front end 61 of the second connection passage 41 be formed so that the first edge portion 61a is formed by the projection or the like. Furthermore, a cutout or the like may be made to face the front side of the rotating direction of the first movable body 11 to extend to the leading end edge 61 of the second connection passage 41 be formed so that the second edge portion 61b is formed by the cutout or the like.

Furthermore, in the compressors according to the first to fifth embodiments, the movable body has 10 the first movable body 11 and the second movable body 12 ; however, the present disclosure is not limited to this example. The moving body 10 may have a cylindrical shape whose diameter is equal to the second shaft hole 23 is so that the drive shaft 3 in the moving body 10 is used.

Furthermore, in the compressor according to any one of the first to fifth embodiments, part of the refrigerant gas that enters the compression chambers once 45a to 45f has been initiated from the compression chambers 45a to 45f through the second connection passage 41 be released. Furthermore, the flow rate of the refrigerant gas released from the compression chambers 45a to 45f in the delivery chamber 29 per rotation of the drive shaft 3 released can be changed so that the flow rate of the refrigerant gas flowing from the compression chambers 45a to 45f is released is changed by changing the connection angle.

Furthermore, in the compressors according to the first to fifth embodiments, the flow rate of the refrigerant gas flowing from the compression chambers is decreased 45a to 45f in the delivery chamber 29 is changed so that the connection angle changes according to the position of the first movable body 11 in the guide window 35a , that is, the position of the moving body 10 in the direction of the axis O , changes; however, the present disclosure is not limited to this example. The flow rate of refrigerant gas released from the compression chambers 45a to 45f in the delivery chamber 29 is released can be changed such that the size of a connection area through which the first connection passages 22a to 22f with the second connection passage 41 are in communication according to the position of the movable body 10 in the direction of the axis O changes.

Furthermore, according to any one of the first to fifth embodiments, the compressor may be configured such that the second movable body 12 not against the section 352 with the second diameter slides, but that a gap between the second movable body 12 and the section 352 is formed with the second diameter.

Furthermore, according to any one of the first to fifth embodiments, instead of the shoes 8a and 8b to use a swash type conversion mechanism in which a swash plate is attached to the rear surface side of the fixed swash plate 5 is supported via a thrust bearing, so that the swash plate and the pistons 7th are coupled to one another by a connecting rod.

Furthermore, in the compressor according to any one of the first to fifth embodiments, the control pressure can be externally controlled by on / off control of an external current supplied from the outside to the control valve 13 is supplied or can be controlled internally without depending on the electric current supplied from the outside. In this situation, if the compressor is designed in such a manner that the valve opening degree is increased by turning off the electric power supplied to the control valve 13 is supplied, the valve opening degree is increased while the compressor is stopped, which increases the control pressure in the control pressure chamber 27 decreased. This allows the compressor to start while the flow rate of the refrigerant gas emanating from the compression chambers 45a to 45f in the delivery chamber 29 is at the minimum, thereby reducing shock that can occur when the compressor is started up.

Furthermore, according to any one of the first to fifth exemplary embodiments, the compressor can perform input-side control such that the control valve 13 changes the flow rate of the refrigerant gas discharged from the discharge chamber 29 to the control pressure chamber 27 through the feed passage 13a is initiated. In this situation, it is possible to promptly cause the control pressure chamber 27 is at a high pressure, and rapidly increasing the flow rate of the refrigerant gas coming from the compression chambers 45a to 45f in the delivery chamber 29 is delivered. In this situation, when the control pressure is controlled externally, so the valve opening degree of the control valve 13 is reduced by turning off the electrical current supplied to the control valve 13 is supplied, the control pressure becomes in the control pressure chamber 27 is decreased because the valve opening degree is decreased while the compressor is stopped. This allows the compressor to start while the flow rate of the refrigerant gas emanating from the compression chambers 45a to 45f in the delivery chamber 29 is at the minimum, thereby reducing shock that can be caused by starting the compressor.

Furthermore, the compressor according to any one of the first to fifth embodiments may be used instead of the control valve 13 To use a three-way valve that controls the degree of opening between the supply passage 13a and the drain passage 13b adjusts.

Furthermore, according to any one of the first to fifth embodiments, the compressor may be configured such that the flow rate of the refrigerant gas flowing from the compression chambers 45a to 45f in the delivery chamber 29 is output is increased so that the control valve 13 the control pressure in the control pressure chamber 27 decreased.

The present disclosure is applicable to air conditioners and the like for a vehicle.

A reciprocating compressor has a moving body ( 10 ), which has a second connection passage ( 41 ) which has a leading end edge ( 61 ) on a front side in a direction of rotation of the movable body ( 10 ) and a rear end edge ( 63 ) on a rear side in the rotating direction relative to the front end edge ( 61 ) Has. The leading end edge ( 61 ) has a first edge section ( 61a) associated with a first connection pass ( 22a to 22f) when a flow rate of a refrigerant flowing from a compression chamber ( 45a to 45f) in a delivery chamber ( 29 ) is delivered, is maximal, and a second edge section ( 61b) belonging to the first connection pass ( 22a to 22f) when the flow rate of the refrigerant is less than the maximum flow rate. The first margin section ( 61a) is on the rear side in the direction of rotation relative to the second edge section ( 61b) located.

Claims (4)

A reciprocating compressor comprising: a housing (1, 17, 19) having a cylinder block (21), a discharge chamber (29), a swash plate chamber (31) and a shaft hole (173, 23), the cylinder block (21) having a plurality of Has cylinder bores (21a to 21f) and a plurality of first communication passages (22a to 22f); a drive shaft (3) rotatably supported through the shaft hole (173, 23); a fixed swash plate (5) which is designed to rotate in the swash plate chamber (31) by rotation of the drive shaft (3) and which has a constant inclination angle with respect to a plane that is perpendicular to the drive shaft (3) ; a plurality of pistons (7) coupled to the fixed swash plate (5), each of the pistons (7) being received in the corresponding cylinder bore (21a to 21f) and a compression chamber (45a to 45f) in the cylinder bore (21a to 21f), the compression chamber (45a to 45f) being in communication with the first communication passage (22a to 22f); a discharge valve (9) configured to discharge a refrigerant from the compression chamber (45a to 45f) into the discharge chamber (29); a movable body (10) provided for the drive shaft (3) and disposed in the shaft hole (23), the movable body (10) being rotatable together with the drive shaft (3) and according to a control pressure relative to the drive shaft (3) is movable in a direction of an axis (O) of the drive shaft (3), the movable body (10) having a second communication passage (41) which extends in a circumferential direction of the movable body (10) and which is intermittently communicates with the first communication passage (22a to 22f) by the rotation of the drive shaft (3) so that the refrigerant is introduced into the compression chamber (45a to 45f) through the first communication passage (22a to 45f), with a flow rate of the refrigerant discharged from the compression chamber (45a to 45f) into the discharge chamber (29) changes according to a position of the movable body (10) in the direction of the axis (O) of the drive shaft (3); and a control valve (13) configured to control the control pressure, the reciprocating compressor being characterized in that the second communication passage (41) has a front end edge (61) which is located on a front side in a rotating direction of the movable body ( 10), and has a rear end edge (63) located on a rear side in the rotating direction relative to the front end edge (61), the front end edge (61) has a first edge portion (61a) corresponding to the first Communication passage (22a to 22f) faces when the flow rate of the refrigerant discharged from the compression chamber (45a to 45f) into the discharge chamber (29) is at a maximum flow rate, and has a second edge portion (61b) corresponding to the first communication passage (22a to 22f) when the flow rate of the refrigerant discharged from the compression chamber (45a to 45f) into the discharge chamber (29) is less than the maximum flow and the first edge portion (61a) is located on the rear side in the rotating direction relative to the second edge portion (61b). Piston compressor after Claim 1 , characterized in that the drive shaft (3) has a guide window (35a) in which the movable body (10) is arranged to be movable in the direction of the axis (O) of the drive shaft (3), the movable body ( 10) has: a first movable body (11) supporting the second Has communication passage (41) and is disposed in the guide window (35a); and a second movable body (12) disposed in the drive shaft (3), the first connection passage (22a to 22f) connected to the second connection passage (41) through the first movable body (11), and the first connection passage ( 22a to 22f) is separated from the second connecting passage (41) by the drive shaft (3). Piston compressor after Claim 1 or 2 , characterized in that the first edge portion (61a) is adjacent to the second edge portion (61b) with gradual changes in the direction of rotation. Piston compressor after Claim 1 or 2 , characterized in that the first edge portion (61a) is adjacent to the second edge portion (61b) with a step (612).

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