JPH0544640A - Swash plate type compressor - Google Patents

Abstract

PURPOSE:To make the whole of a compressor compact by introducing the coolant gas in a swash plate accommodating chamber into a compression chamber through a suction chamber in a double-end piston and discharging the coolant gas discharged from the compression chamber to the outside of the compressor through a discharge passage in a rotary shaft. CONSTITUTION:Suction valves 31 and 40 open, accompanied with the suction operation of a double-end piston 14 for one compression chamber among the front and rear compression chambers 46 and 48, and the coolant gas in the suction chambers 25 and 26 flows into the compression chamber 46 through suction ports 30 and 39. The coolant gas discharged from one compression chamber 46 among the front and rear compression chambers in pair flows into a discharge passage 50 in a rotary shaft 3 in revolution state. The discharge passage 50 communicates to a discharged coolant gas conduit on the outside, and the discharged coolant gas which flows into the discharge passage 50 is discharged into a discharged coolant gas conduit on the outside, together with the coolant gas discharged from the other compression chamber 48. Accordingly, the arrangement radius of the cylinder bores 12 and 13 can be reduced, and the whole of the compression can be made compact.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention converts the rotary motion of a swash plate on a rotary shaft into the reciprocating motion of a double-headed piston, and discharges a refrigerant gas from a compression chamber forming a pair in front and rear by the forward motion of the double-headed piston. The present invention relates to a swash plate compressor.

[0002]

2. Description of the Related Art In this type of swash plate compressor, refrigerant gas in a compression chamber is discharged into a discharge chamber by a forward movement of a double-headed piston, and refrigerant gas in a suction chamber is sucked into the compression chamber by a backward movement of a double-headed piston. It A plurality of double-headed pistons are used and housed in cylinder bores arranged at equal angular intervals around the rotary shaft. The compression chamber is connected to the discharge chamber via the discharge port, and is connected to the suction chamber via the suction port and the suction port. The discharge port is opened and closed by the discharge valve, and the refrigerant gas in the compression chamber is discharged into the discharge chamber while pushing the discharge valve away. The suction port is opened and closed by a suction valve, and the refrigerant gas in the suction chamber is sucked into the compression chamber while pushing the suction valve away.

There are one suction chamber before the cylinder and one suction chamber before the cylinder.
It communicates with the swash plate accommodating chamber via a suction passage in the cylinder block. One discharge chamber is provided before and after the cylinder block, and the discharge chamber communicates with an external discharge refrigerant gas pipe line through a discharge passage in the cylinder block. The external suction refrigerant gas pipeline communicates with the swash plate accommodating chamber through the inlet, and the refrigerant gas is first introduced into the swash plate accommodating chamber by the suction action accompanying the backward movement of the double-headed piston, and the refrigerant gas in the cylinder block It is introduced into the compression chamber through the suction passage and the suction chamber. The refrigerant gas introduced into the compression chamber is discharged to the discharge chamber while being compressed in accordance with the forward movement of the double-headed piston, and is discharged to the discharge refrigerant gas pipe line outside via the discharge passage in the cylinder block.

[0004]

The arrangement interval of the cylinder bores is widened to the extent that the required strength of the cylinder block can be secured. The size of this array interval is proportional to the size of the array radius of the cylinder bores. If the array interval is expanded, the array radius increases, and if the array interval is narrowed, the array radius also decreases. However, normally, one suction passage is provided between the plurality of cylinder bores arranged at equal angular positions around the rotation axis, and one common discharge passage is provided. The presence of the passage leads to a decrease in the strength of the cylinder block. Therefore, as long as the structure in which the suction passage and the discharge passage are provided in the cylinder block is adopted, it is difficult to reduce the array radius of the cylinder bores, and it is difficult to make the compressor compact.

It is an object of the present invention to provide a swash plate type compressor which enables downsizing of the entire compressor.

[0006]

Therefore, according to the present invention,
A pair of suction chambers are provided in the double-headed piston, and an inlet for introducing the refrigerant into the compressor and the suction chamber communicate with each other through a swash plate accommodating chamber, and a double-headed piston has a suction port connecting the suction chamber and the compression chamber. A suction valve that penetrates the end surface of the head and that opens and closes the suction port is attached.

[0007]

The suction valve opens in association with the suction operation of the double-headed piston with respect to one of the front and rear compression chambers, and the refrigerant gas in the suction chamber flows into the compression chamber through the suction port. Refrigerant gas discharged from one of the front and rear of the compression chamber that forms a pair in the front and rear flows into the discharge passage in the rotating shaft in the rotating state. The discharge passage in the rotary shaft communicates with the external discharge refrigerant gas pipe line, and the discharge refrigerant gas flowing into the discharge passage in the rotary shaft is the same as the refrigerant gas discharged from the other front and rear compression chambers. It is discharged to the pipeline.

In the structure in which the refrigerant gas in the swash plate accommodating chamber is directly introduced into the suction chamber in the double-headed piston, the conventional suction passage in the cylinder block is unnecessary, and the discharged refrigerant gas is introduced into the discharge passage in the rotary shaft. The structure does not require the discharge passage in the conventional cylinder block. By omitting the suction passage and the discharge passage in the cylinder block, the arrangement radius of the cylinder bores can be reduced, and the compressor as a whole can be made compact.

If a rotary blade for assisting discharge is provided on the discharge passage in the rotary shaft, the rotary blade rotates integrally with the rotary shaft, and the refrigerant gas in the discharge passage is directed to the external discharge refrigerant gas pipe side. Send out and help. Therefore, the pressure in the communication region between the discharge port and the discharge passage is reduced, and the refrigerant gas in the compression chamber can be discharged without being overcompressed.

Since the discharge passage in the rotary shaft communicates with the surrounding discharge pressure region, the discharge refrigerant gas may leak to the swash plate accommodating chamber along the peripheral surface of the rotary shaft. By interposing a seal ring between the peripheral surface of the rotating shaft and the cylinder block between the plate accommodating chamber, leakage of the discharged refrigerant gas along the peripheral surface of the rotating shaft can be prevented.

The shoe interposed between the swash plate and the double-headed piston is fitted and supported so as not to be disengaged and slidably contactable with the piston, but the fitting recess for fitting and supporting the shoe and the suction chamber are lubricated with lubricating oil. By communicating with the introduction passage, the mist-like lubricating oil in the refrigerant gas is supplied from the lubricating oil introduction passage to between the shoe and the fitting recess. This supply of lubricating oil provides good lubrication between the shoe and the double-headed piston.

If a float valve that floats so as to open the suction port during the intake stroke of the piston and close the suction port during the discharge stroke is used as the suction valve, the float valve moves substantially in parallel to open and close the suction port. Therefore,
The passage cross-sectional area in the suction port can be made larger than that of the suction valve that flexibly deforms, and the suction resistance can be reduced.

If a float valve that floats so as to open the discharge port during the discharge stroke is used as the discharge valve while closing the discharge port during the intake stroke of the piston, the float valve moves substantially in parallel and opens and closes the discharge port. Therefore,
The passage cross-sectional area at the discharge port can be increased as compared with the flexurally deformed discharge valve, and the discharge resistance can be reduced.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment embodying the present invention will now be described with reference to FIGS.
A description will be given based on FIG. Bolt 7 as shown in FIG.
A rotary shaft 3 is rotatably supported by a pair of front and rear cylinder blocks 1, 2 which are fastened and joined together by means of 0 through radial bearings 4, 5, and a swash plate 6 is fixedly supported by the rotary shaft 3. There is. Thrust bearings 8 and 9 are interposed between the end faces of the cylinder blocks 1 and 2 forming the swash plate accommodating chamber 7 and the swash plate 6. Cylinder block 1, 2
The inlets 10 and 11 are formed in the
An external suction refrigerant gas pipe line (not shown) is connected to 11.

As shown in FIGS. 2 to 7, a plurality of cylinder bores 12 and 13 are provided at equidistant angular positions about the rotary shaft 3.
Are formed. As shown in FIG. 1, a double-headed piston 14 is reciprocally housed in a pair of front and rear cylinder bores 12, 13, and a hemispherical shoe is provided between the double-headed piston 14 and both front and rear surfaces of the swash plate 6. 15, 16 are interposed. Therefore, as the swash plate 6 rotates, the double-headed piston 14 moves back and forth in the cylinder bores 12 and 13.

The shoes 15 and 16 are fitted and supported in the supporting recesses 59 and 60 of the double-headed piston 14. Support recess 5
The oil introduction passages 61, 62 are provided in the suction chambers 25, 26 in the reference numerals 9, 60.
It is pierced so as to communicate with. A part of the spherical surface of the shoes 15 and 16 is formed into a flat surface, and gaps 63 and 64 between the flat surface and the support recesses 59 and 60 are always in communication with the oil introduction passages 61 and 62.

A front cover 17 is fastened and joined to the end surface of the cylinder block 1 with bolts 71, and a rear cover 18 is fastened and joined to the end surface of the cylinder block 2 with bolts 72 as well. Both covers 1
Discharge gaps 19 and 20 are formed in 7 and 18, respectively.
The discharge gaps 19 and 20 are connected to the cylinder bores 12 and 13 via the discharge ports 21 and 22 on the covers 17 and 18, respectively. The discharge gap 19 communicates with an external discharge refrigerant gas pipe line (not shown) through the discharge passage 23.

Reference numeral 24 denotes a discharge gap 1 along the peripheral surface of the rotary shaft 3.
9 is a lip seal that prevents refrigerant gas from leaking from the compressor 9 to the outside of the compressor. A pair of suction chambers 2 are provided in the double-headed piston 14.
5, 26 are defined. The suction chambers 25 and 26 are communicated with the swash plate storage chamber 7 via the inlets 27 and 28 on the double-headed piston 14, and the refrigerant gas in the swash plate storage chamber 7 is sucked into the suction chambers via the inlets 27 and 28. It is possible to flow into 25 and 26.

As shown in FIGS. 1, 6 and 7, the swash plate 6 is provided with a plurality of passages 49 in the thickness direction of the swash plate 6. The passages 49 are arranged at a predetermined radial position with the rotation shaft 3 as the center, and the arranged radial positions substantially correspond to the inlets 27 and 28. The passage 49 is provided to smoothly guide the refrigerant gas in the swash plate storage chamber 7 divided into the front and rear by the swash plate 6 to the inlets 27 and 28.

A suction port 30 is formed through the head end surface 29 on the front side of the double-headed piston 14, and a suction valve 31 is provided on the suction port 30. As shown in FIGS. 8 and 10, the intake valve 31 includes a valve seat 32 fitted and fixed to the head end surface 29, a disk-shaped float valve 33 accommodated in the valve seat 32, and a float valve 33. It is composed of a circlip type retainer 34 for accommodating and holding it in the seat 32. As shown in FIG. 9, a pair of through holes 35 are formed in the valve seat 32, and the through holes 35 are opened and closed by the float valve 33. A small opening 36 is formed in the center of the float valve 33 so that the float valve 33 can pass through the opening 3
In the state where 5 is closed, the forehead 36 is closed by the bridge portion 37 between the two passages 35.

Rear end face 3 of double-headed piston 14
8 also has a suction port 39 penetrating therethrough, and the suction port 3
A suction valve 40 similar to the suction valve 31 is interposed on the valve 9. A discharge valve 41 is interposed on the discharge port 21. As shown in FIG. 8, the discharge valve 41 includes a valve seat 42 fitted and fixed to the front cover 17, a disc-shaped float valve 43 accommodated in the valve seat 42, and the float valve 43 in the valve seat 42. And a retainer 44 for accommodating and holding. Valve seat 42, float valve 43 and retainer 44
Have the same shape as the valve seat 32 of the intake valve 31, the float valve 33, and the retainer 34.

A discharge valve 45 similar to the discharge valve 41 is also disposed on the discharge port 22. During the backward stroke of the double-ended piston 14 on the head end surface 29 side, the refrigerant gas in the suction chamber 25 pushes the float valve 33 and is sucked into the compression chamber 46 between the head end surface 29 and the front cover 17. The float valve 33 contacts the retainer 34 and its opening degree is regulated.
During the forward stroke of the head end surface 29 side of the double-headed piston 14, the refrigerant gas in the compression chamber 46 pushes the float valve 43 and is discharged to the discharge gap 19. The opening of the float valve 43 is regulated by contacting the retainer 34.

The other head end surface 38 of the double-headed piston 14
Similar suction and discharge are also performed on the compression chamber 48 side between the rear cover 18 and the rear cover 18 via the suction valve 40 and the discharge valve 45.

One end of the rotary shaft 3 projects outward from the front cover 17, and the other end projects into the discharge gap 20 on the rear cover 18 side. A discharge passage 50 is formed at the axial center of the rotary shaft 3. The discharge passage 50 has a discharge gap 20.
It has an opening.

A lead-out port 51 is formed in a portion of the rotating shaft 3 surrounded by the discharge gap 19 on the front cover 17 side, and the discharge gap 19 and the discharge passage 50 are led out.
Is communicated by.

The radial bearings 4 and 5 are accommodated in annular accommodating gaps 52 and 53, and the oil supply ports 54 and 5 are provided in the portion of the rotary shaft 3 surrounded by the accommodating gaps 52 and 53.
5 is formed. Sealing members 56 and 57 are housed in the housing gaps 52 and 53.

A rotary blade 58 is fitted and fixed in the discharge passage 50. As shown in FIGS. 1, 2 and 3, the rotary shaft 3 rotates in the direction of the arrow α, and the blowing direction of the rotary blades 58 accompanying this rotation is the direction of the arrow β in FIG.

The refrigerant gas in the external suction refrigerant gas pipeline is introduced into the swash plate housing chamber 7, and the refrigerant gas in the swash plate housing chamber 7 is introduced into the inlet port 2.
The suction chambers 25 and 26 are entered via 7 and 28. Inhalation chamber 2
Refrigerant gases 5 and 26 push back the float valves 33 and 43 by the return movement of the double-headed piston 14, while sucking in the suction ports 30,
It is sucked into the compression chambers 46 and 48 from 39. Compression chamber 46,
The refrigerant gas of 48 is discharged from the discharge ports 21, 22 to the discharge gaps 19, 20 while pushing the float valve 43 away by the forward movement of the double-headed piston 14. The refrigerant gas discharged to the discharge gap 20 is discharged from the discharge passage 50 through the opening 65 of the discharge passage 50.
Enter into 0.

The discharge refrigerant gas flowing from the discharge gap 20 into the discharge passage 50 is discharged from the discharge port 5 by the pumping action of the rotary blades 58.
1 to the discharge gap 19. The discharge refrigerant gas in the discharge gap 19 is discharged to the external discharge refrigerant gas pipeline via the discharge passage 23.

One suction passage in the conventional cylinder block is provided between the adjacent cylinder bores, and the presence of such a suction passage reduces the strength of the cylinder block. The discharge passage is also provided in the cylinder block. Therefore, the arrangement interval of the cylinder bores is increased to the extent that the strength of the cylinder block can be secured, and the arrangement interval of the cylinder blocks cannot be narrowed as long as the suction passage and the discharge passage are present in the cylinder block.

The refrigerant gas sucked into the swash plate accommodating chamber 7 passes through the suction chambers 25 and 26 in the double-headed piston 14 to the compression chambers 46 and 4.
The structure in which air is sucked into 8 does not require a plurality of suction passages in the cylinder block in the conventional swash plate compressor. Further, the configuration in which the discharge refrigerant gas discharged into the discharge gap 20 is guided to the discharge passage 23 via the discharge passage 50 in the rotary shaft 3 does not require the discharge passage in the cylinder block in the conventional swash plate compressor. By removing the suction passage and the discharge passage from the cylinder blocks 1 and 2, the cylinder bores 12 and 1
The arrangement interval of 3 can be narrowed. Cylinder bore 1
The reduction of the arrangement interval of 2, 13 leads to the reduction of the arrangement radius of the cylinder bores 12, 13, and the reduction of the diameters of the entire cylinder blocks 1, 2 is achieved. Therefore, it is possible to reduce the diameter and weight of the entire compressor.

Further, in the present invention, the suction chambers provided in the front and rear of the cylinder block are replaced with the suction chambers 25 and 26 in the double-headed piston 14, and this arrangement change also contributes to downsizing of the entire compressor.

The refrigerant gas in the compression chambers 46, 48 is compressed by the compression chamber 4
When the pressure of 6,48 exceeds the pressure of the discharge gaps 19,20, discharge is performed. Since the discharge gap 19 is close to the discharge passage 50, it does not accumulate more pressure than necessary.
Since the distance between the discharge port 51 and the discharge port 51 is large, the discharge resistance between them influences the pressure state of the discharge gap 20. Therefore, in order to prevent the discharge gap 20 from accumulating more than necessary, it is optimal to generate the suction action at the opening 65 of the discharge passage 50. In order to generate such suction action, the refrigerant gas may be forcibly pressure-fed against the discharge resistance of the discharge passage region from the discharge gap 20 to the outlet 51.
In the present embodiment, the rotary blades 58 pump the refrigerant gas in the discharge passage 50 toward the outlet 51.

The rotary blade 58 rotating integrally with the rotary shaft 3 has a small rotational resistance, and the pressure in the discharge gap 20 can be reduced without causing power loss. Due to such pressure reduction in the discharge gap 20, the compression chamber 48
The refrigerant gas is discharged into the discharge gap 20 without being overcompressed. Therefore, discharge pulsation and power loss due to overcompression in the compression chamber 48 are also suppressed. When the rotation speed of the compressor becomes high, the circulation amount of the refrigerant gas increases, and the overcompression state and the discharge pulsation increase in proportion to the rotation speed. However, due to the discharge assisting action of the rotary vanes 58, the compression chamber 4
8 is suppressed, and the effect of suppressing power loss and suppressing discharge pulsation at high speed is high.

The refrigerant gas in the suction chambers 25 and 26 is compressed by the compression chamber 4
When the pressure of 6, 48 falls below the pressure of the suction chambers 25, 26, it is sucked into the compression chambers 46, 48. The flow path resistance in the refrigerant gas flow path from the swash plate storage chamber 7 to the compression chambers 46, 48, that is, the suction resistance determines the pressure state of the suction chambers 25, 26. If this suction resistance is high, suction pulsation will increase and power loss will also increase.

The suction resistance in the refrigerant gas flow path from the swash plate accommodating chamber 7 to the compression chambers 46, 48 is in the suction ports 30, 39 on the head end faces 29, 38 of the double-headed piston 14, which are space limited. Depends solely on inhalation resistance. The suction resistance at the suction ports 30 and 39 is reduced by increasing the cross-sectional area of passage at the suction valves 31 and 40. The float valve 33 that constitutes the suction valves 31 and 40 moves substantially parallel between the valve seat 32 and the retainer 34. As shown in FIG. 8, when the parallel movement distance of the float valve 33 is γ, the outer peripheral length of the float valve 33 is δ, and the inner peripheral length of the float valve 33 is ε, the passage cross-sectional areas of the intake valves 31 and 40 are γ (δ + ε ).

The suction valve in the conventional compressor is a cantilever-supported valve plate, and the valve plate is bent and deformed to open the suction port. The passage cross-sectional area of such an intake valve is approximately half that of the intake valves 31, 40 of this embodiment when the amount of flexural displacement of the valve plate is the same as the parallel displacement of the float valve 33. The cross-sectional area of passage increases if the amount of flexural displacement of the valve element increases, but if such a valve plate is used on the head end faces 29, 38, which are limited in space, the double-headed piston 14
Inevitably increases. Even if the displacement distance of the float valve 33 is equal to or smaller than the bending displacement amount of the valve plate of the conventional intake valve, the intake valve 3
The passage cross-sectional areas of 1 and 40 are larger than those of the conventional intake valve, and the intake resistance can be suppressed without increasing the length of the double-headed piston 14.

Discharge valves 41, 4 having a built-in float valve 43
5 also increases the cross-sectional area of passage in the discharge ports 21 and 22, that is, reduces discharge resistance while suppressing an increase in the thickness of the covers 17 and 18, and contributes to suppression of discharge pulsation and power loss together with the rotary vane 58.

Mist-like lubricating oil is mixed in the refrigerant gas, and this lubricating oil adheres to the peripheral wall of the discharge passage 50. A part of the lubricating oil attached to the peripheral wall of the discharge passage 50 enters the accommodation gaps 52, 53 from the oil supply ports 54, 55 by the centrifugal force caused by the rotation of the rotating shaft 3, and the radial bearings 4, 5 are formed.
Good lubrication.

The mist-like lubricating oil in the refrigerant gas adheres to the wall surfaces of the suction chambers 25 and 26 in the double-headed piston 14. The lubricating oil adhering to the wall surfaces of the suction chambers 25 and 26 is the double-headed piston 14
By the reciprocating motion of the oil introducing passages 61, 62 from the gap 6
Get into 3,64. Therefore, the sliding contact portions between the support recesses 59, 60 and the spherical surfaces of the shoes 15, 16 are lubricated by the lubricating oil supplied from the oil introduction passages 61, 62, so that the shoes 15, 16 and the support recesses 59, 60 are connected to each other. It is possible to prevent the seizure of the sliding contact portion between the two.

The voids 63 and 64 function as oil reservoirs,
Even without the gaps 63 and 64, the sliding contact portions between the shoes 15 and 16 and the support recesses 59 and 60 are satisfactorily lubricated.
The accommodating gap 52 is formed along the outer peripheral surface of the rotary shaft 3 by the discharge gap 19.
The storage gap 53 is connected to the discharge gap 20 along the outer peripheral surface of the rotating shaft 3. That is, the oil supply port 5
The discharge gaps 19 and 20 are in the discharge pressure region even if there are no 4, 55, and the discharge refrigerant gas may leak along the outer peripheral surface of the rotating shaft 3 to the swash plate accommodating chamber 7 in the suction pressure region. However, the swash plate accommodating chamber 7 and the accommodating gaps 52, 53 are sealed by the sealing members 56, 57, and the sealing members 56, 57 are accommodated in the outer peripheral surface of the rotating shaft 3 and the accommodating gaps 52, 57 by the discharge refrigerant gas pressure. It adheres to the peripheral surface of 53. Therefore, the discharged refrigerant gas does not leak to the swash plate accommodating chamber 7 along the outer peripheral surface of the rotating shaft 3.

The present invention is, of course, not limited to the above-mentioned embodiment, but the embodiment shown in FIG. 11 is also possible. In the wall of the rear cover 18 facing the opening 65 of the rotary shaft 3 in this embodiment, a discharge port 66 is provided so as to penetrate, and the discharge port 66 is connected to an external discharge refrigerant gas pipe line (not shown).

The rotating shaft 3 surrounded by the discharge gap 19.
The inlet 67 is formed in the area of
The discharge passage 50 communicates with the discharge passage 50. A rotary blade 68 is fitted and fixed in the discharge passage 50. The rotary shaft 3 rotates in the direction of the arrow α, and the blowing direction of the rotary blades 68 accompanying this rotation is the direction of the arrow ζ in FIG. 11.

The refrigerant gas in the compression chambers 46, 48 is discharged from the discharge ports 21, 22 to the discharge gaps 19, 20 by the forward movement of the double-headed piston 14, and the refrigerant gas discharged to the discharge gap 19 is discharged from the inlet 67 to the discharge passage. Enter in 50. The refrigerant gas discharged from the discharge port 22 to the discharge gap 20 is directly discharged from the discharge port 66.

Since the distance between the discharge gap 19 and the discharge port 66 is large, the discharge resistance between them affects the pressure state of the discharge gap 19. In order to prevent the discharge gaps 19 and 20 from accumulating more than necessary, it is optimal to generate a suction action at the inlet 67 and a suction action from the discharge gap 20 toward the discharge port 66. In order to generate such a suction action, the refrigerant gas may be forcibly pressure-fed against the discharge resistance of the discharge passage region from the discharge gap 19 to the discharge port 66. In this embodiment, the rotary blades 58 pressure-feed the refrigerant gas in the discharge passage 50 toward the discharge port 66.

[0046]

As described above in detail, according to the present invention, the refrigerant gas in the swash plate accommodating chamber is introduced into the compression chamber through the suction chamber in the double-headed piston and is discharged from either one of the front and rear compression chambers. Since the refrigerant gas is discharged to the outside of the compressor via the discharge passage in the rotary shaft, the expansion of the cylinder block due to the existence of the suction passage and the discharge passage in the cylinder block in the conventional swash plate compressor. In addition to the elimination of the diameter, the suction chamber spaces of both the front and rear housings are also unnecessary, thereby achieving an excellent effect that the compressor as a whole can be made compact and lightweight.

[Brief description of drawings]

FIG. 1 is a side sectional view of an entire compressor showing an embodiment embodying the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG.

4 is a cross-sectional view taken along the line CC of FIG.

5 is a cross-sectional view taken along line DD of FIG.

6 is a cross-sectional view taken along the line EE of FIG.

7 is a cross-sectional view taken along the line FF of FIG.

FIG. 8 is an enlarged side sectional view of a discharge valve and a float valve.

9 is a sectional view taken along line GG of FIG.

FIG. 10 is an exploded perspective view of a swash plate, a double-headed piston, and a suction valve.

FIG. 11 is a side sectional view of the entire compressor showing another example.

[Explanation of symbols]

3 ... Rotating shaft, 14 ... Double-headed piston, 19, 20 ... Discharge gap, 21, 22 ... Discharge port, 25, 26 ... Suction chamber, 2
9, 38 ... Head end face, 30, 39 ... Suction port, 3
1, 40 ... Intake valve, 33, 43 ... Float valve, 41, 4
5 ... Discharge valve, 46, 48 ... Compression chamber, 50 ... Discharge passage, 5
6, 57 ... Sealing member, 58, 68 ... Rotor blades, 61, 6
2 ... Oil introduction passage.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Naoya Yokomachi, 2-chome, Toyota-cho, Kariya City, Aichi Stock Company Toyota Industries Corp.

Claims (6)

[Claims] 1. A rotary motion of a swash plate supported on a rotary shaft is converted into a reciprocating motion of a double-headed piston in a cylinder block through a shoe, and a forward-and-backward motion of the double-headed piston causes a pair of compression chambers in the front and rear. In a swash plate compressor that discharges a refrigerant gas from a discharge port while pushing a discharge valve away, a discharge passage is provided in the rotary shaft, and the discharge port and the discharge passage in the rotary shaft are connected to each other, and A pair of suction chambers are provided, and an inlet for introducing refrigerant to the compressor and the both suction chambers are communicated with each other through a swash plate accommodating chamber, and a suction port connecting the suction chambers and the compression chambers is provided with a double-headed piston head A swash plate compressor with a suction valve that opens and closes the suction port while penetrating on the end face. 2. The swash plate compressor according to claim 1, wherein a discharge assisting rotary blade is interposed on the discharge passage in the rotary shaft. 3. The swash plate compressor according to claim 1, wherein the discharge valve is a float valve that closes the discharge port during a suction stroke of a double-headed piston and floats so as to open the discharge port during a discharge stroke. 4. The swash plate compressor according to claim 1, wherein the suction valve is a float valve that opens so that the suction port is opened during a suction stroke of a double-headed piston and is closed so as to close the suction port during a discharge stroke. 5. The shoe is fitted and supported on a double-headed piston so as not to be detachable and slidably contactable, and a fitting recess for fitting and supporting the shoe is penetrated by a lubricating oil introducing passage so as to communicate with the suction chamber. The swash plate compressor according to claim 1, which is provided. 6. A rotary shaft is supported by the cylinder block, and the refrigerant gas is prevented from leaking from the discharge pressure region to the swash plate accommodating chamber along the peripheral surface of the rotary shaft between the rotary shaft and the cylinder block. The swash plate compressor according to claim 1, wherein a seal ring for interposing is provided.