KR101450596B1 - Swash-plate-type compressor - Google Patents

Abstract

In the double-headed piston type swash plate type compressor 10, the front side suction chamber 17 is isolated from the swash plate chamber 25 so as to be positioned between the front side cylinder bores 28 arranged in the circumferential direction. And the cylinder block 11 is formed with a communication path 50a for the suction chamber for communicating the front side suction chamber 17 and the shaft hole 11a. The cylinder block 11 is formed with a plurality of front bore communication passages 50b for communicating the plurality of front cylinder bores 28 with the shaft holes 11a individually. The rotary shaft 22 is provided with a front side rotary valve RF which is integrally rotated with the rotary shaft 22 and in which an introduction groove 22a for sequentially communicating the suction chamber communication path 50a and the front side bore communication path 50b is formed Respectively. Accordingly, a small swash plate type compressor is provided while suppressing the deterioration of pulsation and suction efficiency.

Description

[0001] SWASH-PLATE-TYPE COMPRESSOR [0002]

The present invention relates to a swash plate type compressor having a shaft hole into which a rotating shaft is inserted and a plurality of cylinder bores formed in a circumferential direction around a shaft hole and into which a piston is inserted.

As this type of swash plate type compressor, there is a double-headed piston type swash plate type compressor employing a double-headed piston as a piston, for example, those disclosed in Patent Document 1 can be cited. 11, three cylinder bores 81a are formed in the cylinder block 81 in the swash plate type compressor 80 of the patent document 1, and two cylinder bores 81a are formed in each cylinder bore 81a. ). One suction chamber 83 is formed in the cylinder block 81 so as to be positioned between two adjacent cylinder bores 81a and one discharge chamber 84 is formed between the adjacent cylinder bores 81a, (Not shown). The suction chamber 83 and the discharge chamber 84 can be effectively used to form a space between the adjacent cylinder bores 81a so as to secure the capacity required for suppressing pulsation And the discharge chamber 84 are accommodated in the cylinder block 81, thereby preventing the swash plate type compressor 80 from becoming larger in size.

Although not shown in the drawings, in the swash plate type compressor 80 of Patent Document 1, the refrigerant is sucked from the suction chamber to the cylinder bore 81a by opening the suction port of the reed valve type suction valve. In the suction system using the suction valve, the suction valve is opened or closed based on the pressure difference between the cylinder bore 81a and the suction chamber. When the pressure in the cylinder bore 81a does not decrease to a predetermined pressure, The suction valve may not be opened at a desired timing, and the suction efficiency may be deteriorated.

Therefore, it is effective to adopt a rotary valve that mechanically communicates the cylinder bore and the suction chamber with respect to the swash plate type compressor 80 disclosed in Patent Document 1 in which the size of the body is suppressed, in order to prevent deterioration of suction efficiency .

Japanese Laid-Open Patent Publication No. 9-317633 Japanese Patent Application Laid-Open No. 2007-138925 Japanese Patent Application Laid-Open No. 2007-270790

12, in the swash plate type compressor 90 disclosed in Patent Document 2 as a compressor employing a rotary valve, refrigerant flows from the swash plate chamber 99 through the communication groove 98 to the front housing 93, (Suction chamber) 93a (suction chamber). Therefore, in order to introduce the refrigerant into the suction passage 96 communicating with the cylinder bore 97, the refrigerant in the side of the front housing 93 (the containing chamber 93a) is supplied to the cylinder block 91 . That is, the supply passage 92a extending from the front housing 93 to the cylinder block 91 must be formed in the rotary shaft 92 so that the supply passage 92a is long in axial direction ). Therefore, in the swash plate type compressor 90 of Patent Document 2, by forming the supply passage 92a, the swash plate type compressor 90 becomes larger in size in the axial direction.

13, in the swash plate type compressor 100 disclosed in Patent Document 3 as a compressor employing the same rotary valve, a supply passage 102 is formed in the rotary shaft 101, and a supply passage 102 is formed in the rotary shaft 101, An introduction hole 101a for communicating the inside of the rotary shaft 101 with the outside of the rotary shaft 101 is formed. The suction hole 101a is formed in the swash plate chamber 106 and the supply passage 102 through the suction concavity 105. The suction hole 101a is formed in the cylinder block 104, As shown in Fig.

In Patent Document 3, when the suction recess 105 and the introduction hole 101a communicate with the swash plate chamber 106, the refrigerant in the swash plate chamber 106 flows from the suction recess 105 to the introduction hole 101a and is also introduced into the cylinder bore 108 through the rotary valve 107 from the supply passage 102. [ In Patent Document 3, the introduction hole 101a is formed in the rotary shaft 101 so that the rotary shaft 101 is axially elongated and the suction concavity 105 is formed in the cylinder block 104, The body of the compressor 100 is enlarged in the axial direction. It is also necessary to enlarge the diameter of the rotating shaft 101 in order to ensure the strength of the rotating shaft 101. As a result, the size of the swash plate type compressor 100, And is becoming larger in size.

As described above, since the swash plate type compressors 90 and 100 employing the conventional rotary valve have the swash plate chambers 99 and 106 as the suction chambers, the shape of the rotary valve 107 becomes complicated and large, Resulting in an increase in the size of the swash plate type compressors (90, 100).

SUMMARY OF THE INVENTION An object of the present invention is to provide a swash plate type compressor which is compact while suppressing pulsation and suction efficiency.

In order to achieve the above object, a swash plate type compressor according to an aspect of the present invention includes a cylinder block, a swash plate, a plurality of pistons, a rotary shaft, and a rotary valve. The cylinder block has a shaft hole, a plurality of cylinder bores, a swash plate chamber, and a suction chamber. The shaft hole extends to penetrate the cylinder block. The plurality of cylinder bores are arranged along the circumferential direction around the shaft yoke. The suction chamber is formed between the adjacent cylinder bores and isolated from the swash plate chamber. The swash plate is housed in the swash plate chamber. The plurality of pistons are connected to the swash plate and inserted into the plurality of cylinder bores, respectively. The rotation shaft is inserted into the shaft yoke and rotates integrally with the swash plate. The rotary valve is formed on the rotary shaft so as to rotate integrally with the rotary shaft. The cylinder block has a communication passage for a suction chamber for communicating the suction chamber and the shaft hole, and a plurality of bore communication passages. And the plurality of bore passages individually communicate the plurality of cylinder bores with the shaft bores. And the rotary valve integrally rotates with the rotary shaft to sequentially communicate the suction chamber communication path with the plurality of bore communication paths.

According to this, in the cylinder block, the suction chamber and the cylinder bore are arranged in the circumferential direction around the rotary valve. As a result, even if a rotary valve is adopted as the suction type, the size of the rotary valve and the swash plate type compressor is not increased in the axial direction or the radial direction. Further, since the rotary valve is employed instead of the suction valve as the suction mode, deterioration of the suction efficiency can be prevented as compared with the suction valve.

Preferably, the suction chamber includes a plurality of suction chambers located between adjacent ones of the cylinder bores. The communication passage for the suction chamber includes a plurality of communication passages for the suction chamber which communicate the plurality of suction chambers individually with the shaft holes.

According to this, in the cylinder block, the suction chamber and the cylinder bore are alternately arranged in the circumferential direction around the rotary valve. Therefore, in order to allow the cylinder bore and the suction chamber to communicate with the rotary valve, the supply passage may be formed in a shape extending in a part of the circumferential direction of the rotary valve. Therefore, the shape of the rotary valve formed on the rotary shaft can be simplified, and the axial length can be further shortened.

Preferably, the cylinder block has a plurality of discharge chambers located between adjacent cylinder bores.

According to this, even if the cylinder block is thermally expanded by the high-temperature refrigerant discharged to the discharge chamber, the portions of the thermal expansion are uniformly distributed in the circumferential direction of the housing. As a result, the influence of each cylinder bore and piston on thermal expansion can be reduced.

Preferably, the plurality of discharge chambers are arranged outside the suction chamber in the radial direction of the cylinder block.

Preferably, the cylinder block has a suction port to which the external piping is connected, and a suction passage that communicates the suction hole and the suction chamber, and the suction passage is formed so as to be isolated from the swash plate chamber.

According to this, although the rotary shaft having the rotary valve has heat due to the sliding friction accompanying the rotation, in the suction path of the refrigerant from the suction port to the suction chamber and further to the cylinder bore, the refrigerant flows only through the rotary valve , And is not heat-exchanged with the rotary shaft. Further, since the rotary valve has a short axial length, the heating of the refrigerant in the rotary valve is suppressed to the utmost, and the suction efficiency is increased.

Preferably, the communication path for the suction chamber is constituted by a concave portion formed in the inner wall of the shaft hole, and the concave portion has an opening end (opening end) communicating with the swash plate chamber. A thrust bearing is disposed between the swash plate and the open end of the concave portion, and the thrust bearing closes the opening of the concave portion.

According to this, when the cylinder block is cast, the communication path for the suction chamber can be formed at the same time. Therefore, it is not necessary to cut the communication path for the suction chamber with a drill or the like after the casting of the cylinder block, and the labor of manufacturing the cylinder block can be omitted.

Preferably, the communication path for the suction chamber includes a first recess formed in an inner wall of the suction chamber and having an opening end opening at an end face in the axial direction of the cylinder block, And a second concave portion formed on the inner wall and having an opening end communicating with the swash plate chamber. A thrust bearing is disposed between the swash plate and the open end of the second concave portion, and the thrust bearing closes the opening of the second concave portion.

According to this configuration, not only the communication path for the suction chamber can be formed at the time of casting the cylinder block, but also the passage between the communication path for the suction chamber and the swash plate chamber can be downsized, so that the thrust bearing as the closing member can be downsized.

Preferably, the plurality of cylinder bores are three cylinder bores.

According to this, the capacity of the cylinder bore can be secured within the cylinder block, and the pulsation can be further reduced.

According to the present invention, it is possible to provide a small swash plate type compressor while suppressing the pulsation and the suction efficiency from being lowered.

1 is a cross-sectional view of a double-headed piston type swash plate type compressor according to a first embodiment of the present invention, taken along line 1-1 of Fig.
Fig. 2 is a sectional view taken along line 2-2 of Fig. 3 showing the double-headed piston type swash plate type compressor of the first embodiment.
3 is a cross-sectional view taken along the line 3-3 of Fig. 1 showing the front side discharge chamber and the front side suction chamber.
4 is a sectional view taken along the line 4-4 in Fig. 1 showing the front side cylinder bore, the front side suction chamber, and the front side discharge chamber.
5 is a partial cross-sectional view showing a double-headed piston type swash plate type compressor according to a second embodiment of the present invention.
Fig. 6 is an exploded view of the rotary valve and shaft bush of Fig. 5;
Fig. 7 (a) is a sectional view taken along the line 7a-7a in Fig. 5 showing the cylinder block of Fig. 5 from the front suction chamber side, Fig.
8 is a partial sectional view showing a double-headed piston type swash plate type compressor of another example.
9 is a cross-sectional view showing a double-headed piston type swash plate type compressor of another example.
10 is a development view showing a front-side rotary valve of another example.
11 is a view showing a patent document 1.
12 is a view showing a patent document 2.
Fig. 13 is a view showing the patent document 3. Fig.

(Mode for carrying out the invention)

(First Embodiment)

Hereinafter, a first embodiment in which the swash plate type compressor of the present invention is embodied as a double-headed piston type swash plate type compressor 10 will be described with reference to Figs.

As shown in Figs. 1 and 2, a pair of cylinder blocks 11 and 12 (hereinafter, simply referred to as " compressor " The front housing 13 is joined to the cylinder block 11 on the front side (left side in Fig. 1) through the front side valve / port forming body 15. The rear housing 14 is joined to the cylinder block 12 on the rear side (right side in FIG. 1) through the rear side valve / port forming body 16. The housing H is formed with a pair of cylinder blocks 11, 12 sandwiched between the front housing 13 and the rear housing 14.

The rotary shaft 22 is inserted into the shaft holes 11a and 12a formed in the cylinder blocks 11 and 12 and the rotary shaft 22 is rotatably supported on the inner peripheral surface of the shaft holes 11a and 12a (not shown). The rotary shaft 22 is inserted so as to pass through the insertion holes 15d and 16d formed in the center of the front side valve / port forming body 15 and the rear side valve / port forming body 16. The inner peripheral surface of the front housing 13 and the peripheral surface of the rotary shaft 22 opposed to the inner peripheral surface of the rotary shaft 22 protrude from the front side valve / port forming body 15, and sealed by a shaft sealing device 23 of a lip seal type. The shaft end device 23 is accommodated in a containing chamber 13c defined between the inner circumferential surface of the front housing 13 and the main surface of the rotary shaft 22. [

A swash plate 24, which rotates integrally with the rotating shaft 22, is fixed to the rotating shaft 22. The swash plate 24 is housed in the swash plate chamber 25 formed inside the cylinder blocks 11 and 12 and partitioned between the cylinder blocks 11 and 12. A thrust bearing 26 is interposed between the end face of the cylinder block 11 on the front side and the base portion 24a of the circular plate 24 of the swash plate 24. A thrust bearing 27 is interposed between the end surface of the cylinder block 12 on the rear side and the base 24a of the swash plate 24. The thrust bearings 26 and 27 regulate the movement along the direction of the central axis L of the rotary shaft 22 of the same swash plate 24 with the swash plate 24 interposed therebetween and the thrust bearings 26 and 27, Are pressed against the open end faces of the shaft holes 11a, 12a in the cylinder blocks 11, 12, respectively.

Four front cylinder bores 28 are arranged around the rotary shaft 22 so as to surround the rotary shaft 22 in the cylinder block 11 on the front side as shown in Fig. 1, three rear-side cylinder bores 29 are arranged around the rotary shaft 22 so as to surround the rotary shaft 22 in the cylinder block 12 on the rear side. The front cylinder bore 28 and the rear cylinder bore 29 are paired in the axial direction (forward and backward direction) in which the central axis L extends and the two cylinder bores 28, The piston 30 is inserted. The front side cylinder bore 28 is closed by the front side valve port forming body 15 and the double head piston 30 while the rear side cylinder bore 29 is closed by the rear side valve port forming body 16 ) And the double-headed piston (30).

The rotary motion of the swash plate 24 integrally rotating with the rotary shaft 22 is transmitted to the double head piston 30 through the pair of shoes 31 formed with the swash plate 24 interposed therebetween, Side cylinder bore 28 and the rear-side cylinder bore 29 in the forward and backward directions. The front side compression chamber 28a is partitioned by the double-headed piston 30 and the front side valve port formation body 15 in the front cylinder bore 28 and the front side compression chamber 28b is formed in the rear side cylinder bore 29 Side compression chamber 29a is partitioned by the double-headed piston 30 and the rear-side valve / port-forming body 16. As shown in Fig.

The front housing 13 and the cylinder block 11 are formed with three front suction chambers 17 surrounding the rotating shaft 22 and penetrating the front valve and port forming body 15. As shown in Fig. 4, three front-side suction chambers 17 are disposed one by one between the front-side cylinder bores 28, which are adjacent to each other in the circumferential direction around the shaft hole 11a. The three front suction chambers 17 are arranged at regular intervals on the outer peripheral side of the shaft hole 11a.

1 and 2, one front suction chamber 17 out of the three front suction chambers 17 is connected to the other of the two front suction chambers 17 via a rotation shaft 22 The length along the axial direction is long, and the volume is large. 3, each of the three front-side suction chambers 17 in the front housing 13 communicates with the containing chamber 13c, and three (three in this embodiment) And the front suction chambers 17 are connected to each other to form a connected space.

1 and 3, a front-side discharge chamber 28b is defined between the front housing 13 and the front-side valve / port forming body 15 so as to surround the rotary shaft 22. As shown in Fig. The front side discharge chamber 28b is a space through which the refrigerant from the three front side compression chambers 28a is discharged and is annularly partitioned on the outer peripheral side of the front housing 13. [

In this front-side discharge chamber 28b, portions opposed to the front-side compression chambers 28a are opened through the front-side valve / port forming body 15. In the front-side discharge chamber 28b, the spaces facing the front-side compression chambers 28a communicate with each other through the passages, thereby forming a space connected together.

3 and 4, the cylinder block 11 is formed with three front side discharge chambers 40 communicating with the front side discharge chambers 28b. The front side discharge chamber (40) is connected to the cylinder block (11) on the front side through the front side valve / port forming body (15). The front side discharge chambers 40 formed at three places are arranged around the rotating shaft 22 and formed one by one between the front side cylinder bores 28 adjacent to each other in the circumferential direction of the shaft hole 11a have. Each front-side discharge chamber (40) is formed outside the front suction chamber (17) in the radial direction of the cylinder block (11).

1 and 3, a discharge port 15a is formed at a position corresponding to each front cylinder bore 28 in the front-side valve / port forming body 15, and the discharge port 15a A discharge valve 15b is formed at a position corresponding to the discharge valve 15b. The front side valve / port forming body 15 is formed with a retainer 15c for regulating the open amount of the discharge valve 15b.

Next, the configuration on the rear side will be described.

As shown in Figs. 1 and 2, three rear-side suction chambers 18 are arranged in the rear housing 14 and the cylinder block 12 around the rotating shaft 22 (the shaft hole 12a) And the rear-side valve / port forming body 16, as shown in Fig. The three rear side suction chambers 18 are disposed one by one between the rear side cylinder bores 29 adjacent to each other in the circumferential direction of the shaft hole 12a. One rear side suction chamber 18 of the three rear side suction chambers 18 has a longer length along the axial direction of the rotary shaft 22 than the other two rear suction chambers 18 , The volume is large.

A rear housing side suction chamber 19 is defined between the center of the rear housing 14 and the rear side valve / port body 16. The three rear side suction chambers 18 are communicated with the rear housing side suction chamber 19 so that three rear side suction chambers 18 are connected to each other with the rear housing side suction chamber 19 as a center It is space. The front suction chamber 17 and the rear suction chamber 18 are arranged such that the front suction chamber 17 and the rear suction chamber 18 form one pair in the longitudinal direction in which the center axis L extends. A front suction chamber 17 and a rear suction chamber 18 are formed in the cylinder blocks 11 and 12 with a swash plate 24 interposed therebetween.

A rear side discharge chamber 29b is annularly partitioned to surround the rotary shaft 22 between the rear housing 14 and the rear side valve / port forming body 16. The rear side discharge chamber 29b is a space through which the refrigerant from the three rear side compression chambers 29a is discharged and is partitioned on the outer peripheral side of the rear housing side suction chamber 19. [ In the rear-side discharge chamber 29b, the portions opposed to the respective rear-side cylinder bores 29 through the rear-side valve / port forming body 16 have the same size as the circular shape of the rear-side compression chamber 29a And is opened. Further, in the rear-side discharge chamber 29b, the spaces facing the respective rear-side cylinder bores 29 are communicated with each other by a passage, and are formed as a space connected to each other.

The cylinder block 12 is integrally formed with three rear side discharge chambers 42 communicating with the rear side discharge chambers 29b. The rear side discharge chamber 42 extends from the rear housing 14 through the rear side valve port forming body 16 to the cylinder block 12 on the rear side. The rear side discharge chambers 42 formed at three places are arranged around the shaft holes 12a and formed one by one between the rear side cylinder bores 29 adjacent to each other in the circumferential direction of the shaft holes 12a . Each of the rear-side discharge chambers 42 is formed outside the rear-side suction chamber 18 in the radial direction of the cylinder block 12. The front-side discharge chamber 28b and the rear-side discharge chamber 29b are arranged so as to form one pair in the longitudinal direction in which the central axis L extends.

1, a discharge port 16a is formed at a position corresponding to each of the rear-side discharge chambers 29b in the rear-side valve / port forming body 16, and a discharge port 16a is formed in correspondence with the discharge port 16a A discharge valve 16b is formed. A retainer 16c for regulating the opening degree of the discharge valve 16b is formed in the rear side valve / port forming body 16.

A suction passage 43 is formed in each of the cylinder blocks 11 and 12. The suction passage 43 is formed such that its front opening is connected to the front suction side of the three front side suction chambers 17, And the rear side opening communicates with the rear side suction chamber 18 having the largest volume among the three rear side suction chambers 18. Further, a suction port 44 is formed in the cylinder block 11 on the front side. One end of the suction port 44 is opened on the outer peripheral surface of the cylinder block 11 and the other end is opened on the inner peripheral surface of the suction passage 43. An external piping 32 of an external refrigerant circuit provided outside the compressor 10 is connected to one end opening of the suction port 44. Further, the suction passage 43 is formed in the cylinder block 11, 12 and isolated from the swash plate chamber 25.

Further, the suction passage 43 is formed so as to communicate the suction chambers 17, 18 having the largest volume on the front side and the rear side. The suction passage 43 is located at a position sandwiched in the axial direction by the front side discharge chamber 40 and the rear side discharge chamber 42 located on the outer peripheral side of the both suction chambers 17, Respectively.

2, a discharge passage 45 is formed in each of the cylinder blocks 11 and 12, and an opening on the front side of the discharge passage 45 is connected to three front-side discharge chambers 40 And the opening on the rear side communicates with one of the three rear side discharge chambers. Further, a discharge port 46 is formed in the cylinder block 11. The discharge port 46 has one end opened to the outer surface of the cylinder block 11 and the other end opened to the inner peripheral surface of the discharge passage 45. [ An external piping 33 of an external refrigerant circuit provided outside the compressor 10 is connected to the discharge port 46.

3, the discharge passage 45 is formed in the cylinder block 11, 12 from the position where the suction passage 43 is formed to a position displaced in the circumferential direction of the cylinder block 11, 12 As shown in Fig. More specifically, with respect to the front side discharge chamber 40 and the rear side discharge chamber 42 sandwiching the suction passage 43 in the axial direction, the front side discharge chamber 40 and the rear side discharge chamber 40, And a discharge passage 45 is formed at a position sandwiched by the discharge passage 42 in the axial direction.

The external refrigerant circuit connects the discharge port 46 of the compressor 10 and the suction port 44 through the external piping 32 and 33 when the compressor 10 is used to construct a refrigeration cycle for vehicle air conditioning. The external refrigerant circuit has a condenser, an expansion valve and an evaporator so that they are connected to the discharge port 46 of the compressor 10 on the external refrigerant circuit ).

Next, the suction structure of the compressor 10 will be described.

First, the suction structure on the front side will be described. As shown in Fig. 4, the cylinder block 11 is formed with a communication passage 50a for the suction chamber which communicates the front-side suction chamber 17 and the shaft hole 11a. One end of the communication path for the suction chamber 50a is opened in the front suction chamber 17 and the other end is opened on the sealing surface of the shaft hole 11a. The communication path for the suction chamber 50a extends in the radial direction of the cylinder block 11 with a slight inclination and is formed in the cylinder block 11. [

The cylinder block 11 is formed with a front side bore communication passage 50b for communicating the shaft hole 11a and the front side cylinder bores 28, respectively. The front-side bore communication passage 50b is opened at one end on the sealing main surface of the shaft hole 11a and the other end is opened in the front-side cylinder bore 28. [ The suction chamber communication path 50a and the front side bore communication path 50b are arranged alternately in the circumferential direction of the shaft hole 11a.

As shown in Figs. 1 and 4, an introduction groove 22a is formed in the main surface on the front side of the rotary shaft 22. The introduction groove 22a is recessed in the main surface of the rotary shaft 22, which is a solid shaft, on the front housing 13 side. The introduction groove 22a is open toward the seal main surface of the shaft hole 11a and can communicate with the communication passage 50a for the suction chamber and the communication passage 50b for the front bore individually. The position of the introduction groove 22a is changed in accordance with the rotation of the rotary shaft 22 so that the suction chamber communication path 50a and the front side bore communication path 50b in which the introduction groove 22a is communicated mechanically Respectively.

Therefore, the portion of the rotary shaft 22 surrounded by the seal main surface is a front-side rotary valve RF formed integrally with the rotary shaft 22. The introduction groove 22a is provided so as to communicate the communication path 50a for one suction chamber and the communication path 50b for the front bores adjacent to each other in the circumferential direction of the shaft hole 11a have. The rotation of the rotary shaft 22 causes the suction chamber communication path 50a and the front side bore communication path 50b to communicate with each other through the introduction groove 22a, So that the refrigerant is sucked into the front cylinder bore 28. [ Therefore, in the present embodiment, the introduction groove 22a serves as a supply passage for communicating the front side cylinder bore 28 and the front side suction chamber 17 with the front side rotary valve RF.

Next, the suction structure on the rear side will be described.

As shown in Figs. 1 and 2, the cylinder block 12 is formed with a rear-side introduction passage 51 for communicating the rear-side cylinder bore 29 with the shaft hole 12a. One end of the rear-side introducing passageway 51 is open to the rear-side cylinder bore 29 and the other end is opened on the sealing main surface of the shaft hole 12a. A feed path 22b is formed on the main surface on the rear side of the rotating shaft 22. [ One end of the supply passage 22b is open to the rear housing side suction chamber 19 in the rear housing 14. The other end of the rear-side introduction passage 51 is communicable with the other end of the supply passage 22b. The position of the supply passage 22b is changed in accordance with the rotation of the rotary shaft 22 so that the rear side introduction passage 51 communicating with the supply passage 22b is mechanically switched. Therefore, the portion of the rotating shaft 22 surrounded by the seal main surface is the rear-side rotary valve RR formed integrally with the rotating shaft 22.

Next, the operation of the compressor 10 having the above-described configuration will be described.

The refrigerant is sucked into the suction passage 43 through the suction port 44 and the refrigerant is supplied to the front suction chamber 17 and the rear suction chamber 18, respectively. When the front cylinder bore 28 is shifted to the intake stroke, as shown in Fig. 4, one intake chamber communication passage 50a is opened through the introduction groove 22a of the front-side rotary valve RF, And the adjacent front bore communication passage (50b) of the communication passage (50a) for the suction chamber communicate with each other. Then, the refrigerant is sucked into the front cylinder bore 28 via the front side rotary valve RF from the front side suction chamber 17.

As the rotary shaft 22 rotates, the introduction groove 22a is non-communicated with the communication passage 50a for the suction chamber, and the suction chamber communication path 50a and the front-side bore communication passage 50b And when the front cylinder bore 28 is shut off, the front cylinder bore 28 shifts to the compression stroke and the discharge stroke. Then, the refrigerant in the front side compression chamber 28a pushes the discharge valve 15b from the discharge port 15a and is discharged to the front discharge chamber 28b. The refrigerant discharged to the front side discharge chamber 28b passes through the discharge passage 45 and the discharge port 46 from the front side discharge chamber 40 and flows out to the external refrigerant circuit.

On the other hand, on the rear side, when the rear-side cylinder bore 29 is shifted to the intake stroke in the state where the refrigerant is supplied to the rear housing side suction chamber 19, the rear- The supply passage 22b communicating with the suction chamber 19 communicates with one or two rear side introduction passages 51. [ The refrigerant is supplied from the rear housing side suction chamber 19 to the rear side intake passage 51 through the rear side rotary valve RR and the rear side cylinder 51 communicates with the rear side introduction passage 51. [ The refrigerant is sucked into the bore 29.

As the rotary shaft 22 rotates, the supply passage 22b becomes non-communicating with the rear-side introduction passage 51, and the communication between the rear-side introduction passage 51 and the rear housing-side suction chamber 19 And the rear cylinder bore 29 is shut off, the rear cylinder bore 29 shifts to the compression stroke and the discharge stroke. Then, the refrigerant in the rear side compression chamber 29a pushes the discharge valve 16b from the discharge port 16a and is discharged to the rear side discharge chamber 29b. The refrigerant discharged to the rear-side discharge chamber 29b passes through the discharge passage 45 and the discharge port 46 from the rear-side discharge chamber 42 and flows out to the external refrigerant circuit.

Therefore, according to the present embodiment, the following advantages can be obtained.

(1) In the double-headed piston type swash plate type compressor 10, three front cylinder bores 28 are formed around the shaft hole 11a of the cylinder block 11, Side suction chambers 17 are disposed one by one between the side cylinder bores 28, as shown in Fig. That is, the front-side cylinder bore 28 and the front-side suction chamber 17 are arranged alternately around the shaft hole 11a. A communication path 50a for the suction chamber for communicating the front side suction chamber 17 and the shaft hole 11a and a communication path for the front side bore communicating the front side cylinder bore 28 and the shaft hole 11a, And the front and rear bore communication passages 50a and 50b are arranged alternately in the circumferential direction of the shaft hole 11a in the cylinder block 11 and the suction chamber communication path 50a and the front side bore communication path 50b. The refrigerant in each of the front suction chambers 17 is introduced directly into the introduction groove 22a through the suction chamber communication path 50a in the cylinder block 11 and then flows through the front bore communication passage 50b And is sucked into the front-side cylinder bore 28 through the front- Therefore, in order to make the front side cylinder bore 28 and the front side suction chamber 17 adjacent to each other in the circumferential direction communicate with the front side rotary valve RF, the introduction groove 22a is formed in the circumferential direction of the rotary valve RF As shown in Fig. Therefore, since the shape of the front-side rotary valve RF can be simplified, the length in the axial direction of the front-side rotary valve RF can be shortened. As a result, even if the front-side rotary valve RF is employed as the suction method of the compressor 10 having the front-side suction chamber 17 in the cylinder block 11, even if the body of the compressor 10 is in the axial direction, Direction. Since the front cylinder bore 28 and the front side intake chamber 17 are mechanically communicated with each other by employing a rotary valve instead of a suction valve as the intake system, . In addition, since three cylinder-side suction chambers 17 are formed in the cylinder block 11, the capacity of the suction chamber can be sufficiently secured, and the pulsation can be suppressed.

(2) One front suction chamber 17 is formed between the front cylinder bores 28 adjacent to each other in the circumferential direction of the shaft hole 11a. The cylinder block 11 was provided with a communication passage 50a for the suction chamber for communicating the front suction chambers 17 and the introduction grooves 22a of the front rotary valve RF. The refrigerant in each of the front suction chambers 17 can be directly introduced into the introduction groove 22a through the communication path for suction room 50a. It is not necessary to form the introduction groove 22a extending from the front housing 13 to the cylinder block 11 on the rotary shaft 22 since it is not necessary to once introduce the refrigerant into the suction pressure region of the front housing 13. [ . Therefore, the rotary shaft 22 is supported on the shaft hole 11a (seal peripheral surface) before and after the axial direction of the introduction groove 22a, thereby securing the bearing area of the rotary shaft 22 and improving wear resistance.

(3) Similarly to the front-side suction chamber 17, one rear-side suction chamber 18 is formed between the adjacent rear-side cylinder bores 29 so as to surround the rotary shaft 22. Therefore, the suction chambers 17 and 18 are formed in the radial direction of the cylinder blocks 11 and 12 on the front side and the rear side, respectively, and the increase in the size of the compressor 10 in the axial direction can be suppressed.

(4) A front side discharge chamber 28b is formed in the front housing 13 and a rear side discharge chamber 29b is formed in the rear housing 14. The front side discharge chamber 28b is provided with three front side discharge And the rear side discharge chamber 29b is communicated with the three rear side discharge chambers 42. As shown in Fig. Each of the discharge chambers 40 and 42 is disposed between the adjacent cylinder bores 28 and 29, respectively. Therefore, the capacity of each of the discharge chambers 40, 42 in the cylinder blocks 11, 12 can be largely secured, and the pulsation can be further reduced.

(5) Each of the discharge chambers 40, 42 is disposed outside the suction chambers 17, 18 in the radial direction of the cylinder block 11, 12. Therefore, even if the cylinder blocks 11 and 12 are thermally expanded by the high-temperature refrigerant discharged to the discharge chambers 40 and 42, the portions of thermal expansion are evenly distributed in the radial direction of the cylinder blocks 11 and 12. [ As a result, the influence of the double-headed piston 30 on the cylinder bores 28, 29 due to thermal deformation can be reduced.

(6) Each of the discharge chambers 40, 42 is disposed one by one between the respective cylinder bores 28, 29. Therefore, even if the cylinder blocks 11 and 12 are thermally expanded by the high-temperature refrigerant discharged to the respective discharge chambers 40 and 42, the portions of the thermal expansion are evenly distributed in the circumferential direction of the cylinder blocks 11 and 12. As a result, the influence of the double-headed piston 30 on the cylinder bores 28, 29 due to thermal deformation can be reduced.

(7) A suction port 44 is formed in the cylinder block 11 and a suction passage 43 communicating with the front suction chamber 17 and the rear suction chamber 18 is provided in the cylinder block 11, 12 Respectively. Therefore, when the refrigerant is sucked into each of the suction chambers 17 and 18, the refrigerant does not pass through the swash plate chamber 25. Therefore, the refrigerant sucked into each of the suction chambers 17 and 18 is heated by the blow-bye gas flowing into the swash plate chamber 25 or the rotating shaft 22 heated by the sliding friction, Can be prevented.

(8) The front-side suction chamber 17 and the rear-side suction chamber 18 are axially paired, and the front-side discharge chamber 40 and the rear-side discharge chamber 42 are also paired in the axial direction. The front rotary valve RF is employed as a suction method for the front cylinder bore 28 and the rear rotary valve RR is employed as a suction method for the rear cylinder bore 29. [ Therefore, since the suction structure is the same between the front side and the rear side, it is possible to suppress the occurrence of vibration and abnormal noise caused by the difference in suction structure between the front side and the rear side.

(9) One front suction chamber 17 is formed between the front cylinder bores 28 adjacent to each other in the circumferential direction so as to surround the shaft holes 11a. The cylinder block 11 is provided with a suction chamber communication path 50a for communicating the front side suction chamber 17 and the front side rotary valve RF introduction groove 22a with each other, And the front-side bore communication passage (50b) for communicating the side cylinder bore (28). The refrigerant in each of the front suction chambers 17 is sucked into the front cylinder bore 28 through the suction chamber communication path 50a, the introduction groove 22a and the front side bore communication path 50b So that the suction of the refrigerant from the front side suction chamber 17 to the front side cylinder bore 28 in the cylinder block 11 can be completed. Therefore, as compared with the case where the refrigerant is sucked into the front cylinder bore 28 through the front housing 13 and the groove extended into the swash plate chamber 25, the contact area between the refrigerant and the introduction groove 22a can be shortened have. As a result, it is possible to reduce the increase in suction overheating accompanied by the lengthening of the contact area between the refrigerant and the introduction groove 22a, thereby preventing deterioration of the suction efficiency.

(10) The rotary shaft 22 has heat due to sliding friction with the shaft holes 11a, 12a and the like, but is in contact with the front side suction chamber 17 and the front side cylinder bore 28 In the suction path of the refrigerant, when the refrigerant passes through the introduction groove 22a, it is heat-exchanged with the rotary shaft 22 through the front-side rotary valve RF. However, since the length of the introduction groove 22a in the axial direction is short, the heating of the refrigerant in the front-side rotary valve RF is suppressed to the utmost, and the suction efficiency is increased.

(Second Embodiment)

Next, a second embodiment of the present invention will be described with reference to Figs. 5 to 7. Fig. The same components as those in the first embodiment are denoted by the same reference numerals, and redundant explanations thereof are omitted or simplified.

As shown in Figs. 5 and 7A, the first end face 11b, which is the surface of the cylinder block 11 on the front housing 13 side, is located at a position outside the shaft yoke 11a And the first concave portion 60 are formed to correspond to the front suction chambers 17, respectively. The first concave portion 60 is formed so as to extend in the radial direction from the inner wall of each front suction chamber 17 in the cylinder block 11. [ One end of the first concave portion 60 is opened to the first end face 11b which is the surface in the axial direction of the cylinder block 11 and is connected to the opening of each front side suction chamber 17. [ The other end of the first concave portion 60 is positioned in the axial length of the front suction chamber 17 and does not penetrate the cylinder block 11 in the axial direction. The first concave portion 60 is recessed from the first end face 11b toward the second end face 11c.

5 and 7 (b), in the second end surface 11c, which is the surface on the side of the swash plate chamber 25 in the axial direction of the cylinder block 11, And is formed so as to correspond to the front suction chamber 17. The second concave portion 61 is formed in the cylinder block 11 so as to extend in the radial direction from the inner wall of the shaft hole 11a. One end of the second concave portion 61 is opened to the second end face 11c of the cylinder block 11 and is connected to the opening of the shaft hole 11a. The other end of the second concave portion 61 is located in the axial length of the shaft hole 11a and does not penetrate the cylinder block 11 in the axial direction. The second concave portion 61 is recessed from the second end face 11c toward the first end face 11b. The opening of the second concave portion 61 on the side of the second end face 11c (on the side of the swash plate chamber 25) is closed by the thrust bearing 26. [

In the cylinder block 11, the first concave portion 60 and the second concave portion 61 are connected to each other to communicate with each other, thereby forming a communication path 62 for the suction chamber. One end of the suction chamber communication path 62 is formed by the opening of the first recess 60 on the side of the front suction chamber 17 and the other end of the suction chamber communication path 62 is formed by the second concave Is formed by an opening on the shaft hole 11a side in the portion 61. [ The front suction chamber 17 and the introduction groove 22a can communicate with each other through the communication path 62 for the suction chamber. The opening end of the swash plate chamber 25 side is closed by the thrust bearing 26 and the space between the suction chamber communication path 62 and the swash plate chamber 25 is closed by the seal . The first concave portion 60 and the second concave portion 61 are formed in combination with the front side suction chamber 17 when the cylinder block 11 is manufactured by casting.

6 is a view of the front side rotary valve RF being expanded in the circumferential direction. The outer surface of the front side rotary valve RF and the front side rotary valve RF are inserted and supported by the outline indicated by the solid line And represents a shaft hole 11a. The introduction grooves 22a are shown in these outline lines. 6 shows the front side bore communication passage 50b which is open to the shaft hole 11a and communicates with the front side cylinder bores 28 and which is provided with a shaft hole 11a And the communication path 62 for the suction room (the area in which the first recess 60 and the second recess 61 overlap each other) communicating with the respective front suction chambers 17 is shown.

The front bore communication passage 50b and the suction chamber communication passage 62 are arranged alternately along the circumferential direction of the shaft hole 11a as shown in Fig. The introduction groove 22a is formed so as to extend in the circumferential direction of the rotary shaft 22 in order to communicate the suction chamber communication path 62 and the front side bore communication path 50b by the introduction groove 22a. .

Therefore, according to the second embodiment, in addition to the advantages (1) to (10) described in the first embodiment, the following advantages can be obtained.

(11) Since the suction chamber communication path 62 has a long rectangular shape in the axial direction, the communication hole 62 for the suction chamber and the communication path 50b for the front side bore are formed in the shaft hole 11a, And are arranged alternately in the circumferential direction. Therefore, in order to make the front side cylinder bore 28 and the front side suction chamber 17 adjacent to each other in the circumferential direction communicate with the front side rotary valve RF, the front side bore communication passages 50b and the communication path for the suction chamber 62 through the introduction groove 22a. Therefore, the introduction groove 22a may be formed in the front-side rotary valve RF so as to extend in a part of the circumferential direction of the front-side rotary valve RF. Therefore, the shape of the front-side rotary valve RF formed on the rotary shaft 22 can be simplified, and the length in the axial direction can be shortened. As a result, even if the front-side rotary valve RF is employed as the suction method of the compressor 10 having the front-side suction chamber 17 in the cylinder block 11, the size in the axial direction is not increased.

(12) The communication path for the suction chamber 62 is formed collectively together with the front suction chamber 17 when casting the cylinder block 11. [ Therefore, it is possible to reduce the labor of manufacturing the cylinder block 11 as compared with the case where the cylinder block 11 is cast and then the suction chamber communication path 62 is formed by cutting with a drill or the like.

(13) The communication path 62 for the suction chamber is formed by connecting a first concave portion 60 extending from the first end face 11b and a second concave portion 61 extending from the second end face 11c do. The opening area of the second recess 61 can be reduced and the opening of the second recess 61 can be made relatively small in comparison with the case where the second recess 61 is formed only in the communication path for the suction chamber. The thrust bearing 26 can be closed.

The above embodiment may be modified as follows.

The communicating path 62 for the suction chamber is formed by the first concave portion 60 extending from the first end face 11b of the cylinder block 11 and the second concave portion 60 extending from the second end face 11c 61 are connected, but the present invention is not limited to this. 8, if the outer diameter of the thrust bearing 26 is sufficiently large, even if the communication passage for the suction chamber is formed by only the second recess 66 extending from the second end face 11c of the cylinder block 11 good. The second concave portion 66 allows direct communication between the front suction chamber 17 and the introduction groove 22a.

In addition to the path through the intake-side communication path 62 by the front-side rotary valve RF and the front-side bore communication path 50b as a suction path for the refrigerant gas to the front-side cylinder bore 28, It is also possible to form a path via an in-shaft passage 65 communicating with the rear housing side suction chamber 19 as shown in Fig. In this case, the refrigerant is sucked into the front side cylinder bore 28 only by passing the in-shaft passage 65 from the rear housing side suction chamber 19. The refrigerant is sucked from the front side suction chamber 17 through the suction chamber communication The refrigerant is sucked into the front-side cylinder bore 28 even through the passage 62. Therefore, the diameter of the axial passage 65 can be reduced. Therefore, the rotary shaft 22 and the rotary valve RF can be downsized in the radial direction, and the overall size of the compressor 10 can also be reduced.

In the embodiment, the rotary valve is employed as the suction method on the front side and the rear side, but the suction side may be a suction valve instead of a rotary valve on the rear side.

The refrigerant in the rear side suction chamber 18 is collected in the rear housing side suction chamber 19 from the rear housing side suction chamber 19 through the rear side rotary valve RR to the rear side It is sucked into the cylinder bore 29, but the present invention is not limited to this. The rear side suction chambers 18 and the shaft holes 12a are communicated with each other through the communication holes and the shaft holes 12a and the rear side cylinder bores 29 are introduced individually through the introduction passages And the refrigerant may be sucked from the rear side suction chamber 18 to the rear side cylinder bore 29 via the communication passage and the introduction hole and introduction passage of the rear side rotary valve RR.

The intake port 44 is formed in the cylinder block 11 on the front side and the intake port 44 is formed in the other portion in the housing H such as the cylinder block 12 on the rear side, .

The refrigerant having passed through the suction port 44 is supplied to the front suction chamber 17 and the rear suction chamber 18 through the suction passage 43 formed in the cylinder blocks 11 and 12. However, The refrigerant having passed through the swash plate chamber 44 may be supplied to the front suction chamber 17 and the rear suction chamber 18 via the swash plate chamber 25. [

In the embodiment, three front-side discharge chambers 40 are disposed between the adjacent front-side cylinder bores 28, but the front-side discharge chambers 40 are collectively formed at one or two positions There may be. 10, a part of the introduction groove 22a is connected to the rotary shaft 22 so that the suction chamber communication path 62 always communicates with the introduction groove 22a regardless of the rotation angle of the rotary shaft 22, And is formed in an annular shape that makes one round of the main surface on the front side of the front side.

The three rear-side discharge chambers 42 are disposed between the adjacent rear-side cylinder bores 29, but the rear-side discharge chambers 42 may be collectively formed at one or two positions.

In the embodiment, three rear-side suction chambers 18 are formed and one rear-side suction chamber 18 is disposed between the adjacent rear-side cylinder bores 29. However, the present invention is not limited to this . The suction space on the rear side may be only the rear housing side suction chamber 19 or the rear side suction chamber 18 may be formed in one or two places.

The front side suction chamber 17 communicating with the suction passage 43 is made larger in volume than the other two front side suction chambers 17 in the embodiment, The volume may be larger than the volume of the front suction chamber 17 communicating with the suction passage 43. [ Since the refrigerant is directly supplied from the suction passage 43 to the front suction chamber 17 communicating with the suction passage 43, the refrigerant is smoothly supplied to the front cylinder bore 28 Therefore, the volume may be small. On the other hand, in the other two front suction chambers 17, since refrigerant supplied to the housing chamber 13c is once supplied to the front cylinder bore 28, the refrigerant supplied to the front cylinder bore 28 It is preferable that a large volume of refrigerant is supplied.

The three front suction chambers 17 may have the same volume.

The front side suction chamber 17 and the front side discharge chamber 40 are formed over both the front housing 13 and the cylinder block 11 but may be formed only in the cylinder block 11 .

The rear side suction chamber 18 and the rear side discharge chamber 42 are formed on both sides of the rear housing 14 and the cylinder block 12 but may be formed only in the cylinder block 12 .

The swash plate type compressor is used as a single-headed piston, and the swash plate type compressor is mounted on the swash plate 24 so that the double-headed piston 30 is used as a single-headed piston, The compressor may be changed.

RF: Front-side rotary valve as rotary valve
10: Double-headed piston type swash plate compressor
11, 12: Cylinder block
11a, 12a: Football yoke
17: Front suction chamber
18: Rear side suction chamber
22:
22a: introduction home
24: Swash plate
25: swash plate
26, 27: thrust bearing
28: front cylinder bore as cylinder bore
28b: a front-side discharge chamber as a discharge chamber
29: rear cylinder bore as cylinder bore
29b: rear discharge chamber as a discharge chamber
30: Double head piston
32, 33: External piping
40: front discharge chamber as discharge chamber
42: Rear side discharge chamber as a discharge chamber
43: suction passage
44: inlet
50a: communication passage for the suction chamber
50b: a communication passage for the front side bore
60: first concave portion
61, 66: second concave portion
62: communication passage for the suction chamber

Claims (8)

A cylinder block having a shaft bore, a plurality of cylinder bores, a swash plate chamber, and a suction chamber, wherein the shaft bores extend through the cylinder block, the plurality of cylinder bores being circumferentially arranged around the shaft bore Wherein the suction chamber is formed between the adjacent cylinder bores and isolated from the swash plate chamber,
A swash plate housed in the swash plate chamber,
A plurality of pistons pierced on the swash plate and inserted into the plurality of cylinder bores, respectively,
A rotating shaft integrally rotating with the swash plate when the swash plate is inserted into the swash plate,
And a rotary valve formed on the rotary shaft so as to rotate integrally with the rotary shaft,
Wherein the cylinder block has a communication passage for a suction chamber which communicates the suction chamber and the shaft hole and a plurality of bore communication passages for respectively communicating the plurality of cylinder bores with the shaft bores,
And the rotary valve integrally rotates with the rotary shaft to sequentially communicate the suction chamber communication path with the plurality of bore communication paths. The method according to claim 1,
Wherein the suction chamber includes a plurality of suction chambers located between adjacent ones of the cylinder bores,
Wherein the communication passage for the suction chamber includes a plurality of communication passages for the suction chamber which communicate the plurality of suction chambers individually with the shaft holes. 3. The method of claim 2,
Wherein the cylinder block has a plurality of discharge chambers located between adjacent cylinder bores. The method of claim 3,
Wherein the plurality of discharge chambers are arranged outside the suction chamber in the radial direction of the cylinder block. The method according to claim 1,
Wherein the cylinder block has a suction port to which external piping is connected and a suction passage that communicates with the suction hole and the suction chamber,
And the suction passage is formed to be isolated from the swash plate chamber. The method according to claim 1,
Wherein the suction chamber communication path is formed by a recess formed in an inner wall of the shaft hole, the recess has an opening end communicating with the swash plate chamber,
A thrust bearing is disposed between the swash plate and the open end of the concave portion,
And the thrust bearing closes the opening of the recess. The method according to claim 1,
Wherein the suction chamber communication path includes a first concave portion formed on an inner wall of the suction chamber and having an opening end opened to an end face in an axial direction of the cylinder block, And a second concave portion having an opening end communicating with said swash plate chamber,
A thrust bearing is disposed between the swash plate and the open end of the second concave portion,
And the thrust bearing closes the opening of the second recess. 8. The method according to any one of claims 1 to 7,
Wherein the plurality of cylinder bores are three cylinder bores.

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