JP2017008728A - Swash plate type gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To be able to shorten a time up to the supply of a lubricant to a slide portion even if the lubricant is in a decreased state, in a swash plate type gas compressor.SOLUTION: A compressor (100) comprises: swash plates 20 which are fixed to a rotating shaft 9 in postures inclined to an axial line C of the rotating shaft 9, and arranged so that external peripheral faces 20C in radial directions with the axial core C as a center are immersed in a lubricant R which is accumulated in a crank chamber 5; and piston shoes (16) which are arranged at a piston (11), contact with surfaces 20a, 20b of the swash plates 20, and slide between the rotating swash plates 20. The swash plates 20 have passages 21 for making the external peripheral faces 20C (external peripheral portions) communicate with portions 20A, 20B with which the piston shoes 16 of the surfaces 20a, 20b contact, and the passages 21 are inclined to a direction in which openings 21c at the external peripheral faces 20C are shifted to a front side of a rotation direction M by an inclination angle θ with respect to the radial directions of the swash plates 20.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a swash plate type gas compressor.

A gas compressor that compresses a gas such as a refrigerant gas into a high-pressure compressed gas is used in an air conditioning system (hereinafter referred to as an air conditioning system).
As this gas compressor, a so-called swash plate type gas compressor is known.
The swash plate type gas compressor includes a swash plate fixed to the rotary shaft in a posture inclined with respect to the axis of the rotary shaft, and a cylinder bore formed around the rotary shaft along the axial direction of the rotary shaft. A plurality of pistons that reciprocate inside are arranged. A compression chamber for compressing gas is formed by the cylinder bore and the piston.

Each piston is provided with a piston shoe, and the piston shoe is disposed in contact with the surface of the swash plate. When the swash plate is rotated by the rotation of the rotary shaft, the axial position of the swash plate in contact with each piston shoe changes, and each piston reciprocates along the axial direction, and is sucked into the compression chamber. The compressed gas is compressed.
Here, the swash plate is disposed in the crank chamber inside the housing of the gas compressor, and lubricating oil is stored in the crank chamber. Part of the swash plate is immersed in the lubricating oil, and the lubricating oil repelled by the rotation of the swash plate sprinkles the part where the swash plate and piston shoe slide (the sliding surface that is the surface of the swash plate) The sliding portion is lubricated (see, for example, Patent Document 1).

JP 2007-205315 A

The technique described in Patent Document 1 is in a state where the lubricating oil is immersed only in the outer peripheral portion of the swash plate when the lubricating oil inside the gas compressor is reduced. For this reason, there is a problem that it takes a long time until the lubricating oil is supplied to the sliding portion after the gas compressor is started.
The present invention has been made in view of the above circumstances, and even in a state where the lubricating oil is reduced, the swash plate type gas compression capable of shortening the time until the lubricating oil is supplied to the sliding portion. The purpose is to provide a machine.

  The present invention is fixed to the rotating shaft in a posture inclined with respect to the axis of the rotating shaft rotating with respect to the crank chamber, and at least an outer peripheral portion in the radial direction centering on the axis is accumulated in the crank chamber. Piston which is provided on a swash plate disposed so as to be immersed in the lubricating oil and a piston which reciprocates along the axis, and which slides between the rotating swash plate in contact with the surface of the swash plate The swash plate has a passage through which an outer peripheral portion and a portion of the surface that is in contact with the piston shoe are in contact with each other, and the passage has an opening in the outer peripheral portion with respect to a radial direction of the swash plate. Is a swash plate type gas compressor that is inclined in a direction toward the front side in the rotation direction.

  According to the swash plate type gas compressor according to the present invention, even when the lubricating oil is reduced, the time until the lubricating oil is supplied to the sliding portion can be shortened.

It is sectional drawing which shows the longitudinal cross-section of the variable displacement type compressor which is an example of the swash plate type gas compressor which concerns on this invention. It is a schematic diagram which shows the detailed structure of a swash plate, (A) is the figure seen in the axial center C direction, (B) shows the side view by the arrow B in (A), respectively. FIG. 3 is a view corresponding to FIG. 2 (A) showing an example in which an opening on the outer peripheral surface of the passage shown in FIG. It is a schematic diagram which shows the swash plate which has the channel | path formed by the single linear space, (A) is the figure seen in the axial center C direction, (B) is the side view by the arrow D in (A). , Respectively. It is a schematic diagram which shows the swash plate in which the channel | path of the groove | channel was formed in one surface, and the channel | path of the groove | channel was formed in the other surface, (A) is the figure seen in the axial center C direction, (B) is (A) The side view by arrow E in FIG. A slant having a configuration in which a plurality of radial passages corresponding to the radially extending passages shown in FIG. 5 are connected to an annular passage at the center side end (opening of the passage at the portion where the piston shoe contacts). It is the schematic diagram which shows a board, (A) is the figure seen in the axial center C direction, (B) shows the side view by the arrow F in (A), respectively.

  Embodiments of a swash plate type gas compressor according to the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view showing a longitudinal section of a variable displacement compressor 100 which is an example of a swash plate type gas compressor according to the present invention.

[Embodiment 1]
<Compressor configuration>
The illustrated compressor 100 is configured as a part of an air conditioning system that performs cooling using, for example, heat of vaporization of a cooling medium. It is provided on the circulation path of the cooling medium together with a condenser, an expansion valve, an evaporator and the like (all of which are not shown) as other components of the air conditioning system. In addition, this air conditioning system is an air conditioner for adjusting the temperature in the interior of a vehicle (such as an automobile), for example.

  The compressor 100 compresses the refrigerant gas G as a gaseous cooling medium taken from the evaporator, and supplies the compressed refrigerant gas G to the condenser. The condenser liquefies the compressed refrigerant gas G and sends it to the expansion valve as a high-pressure liquid refrigerant. The high-pressure and liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from the surrounding air and vaporizes in the evaporator, and cools the air around the evaporator by removing the heat of vaporization. The refrigerant gas G that has been vaporized into gas is returned to the compressor 100.

As shown in FIG. 1, the compressor 100 includes a cylinder block 1, a front head 2, a rear head 3, and an electromagnetic clutch 4.
The cylinder block 1, the front head 2 and the rear head 3 constitute a housing of the compressor 100.
The front head 2 is joined to the front end surface (the left end surface in the drawing) of the cylinder block 1 and forms a crank chamber 5 therein.
The rear head 3 is joined to a rear end surface (right end surface in the drawing) of the cylinder block 1 via a valve plate 6, and forms a suction chamber 7 and a discharge chamber 8 therein.

The electromagnetic clutch 4 is fixed to the nose portion of the front head 2, and transmits the rotational driving force transmitted from the engine or the like of the vehicle on which the compressor 100 is mounted to the rotating shaft 9.
Inside the cylinder block 1, a plurality of (for example, six) cylinder chambers 10 are formed around the rotating shaft 9 and arranged at equal angular intervals in the circumferential direction. A piston 11 is accommodated in each cylinder chamber 10 so as to be able to reciprocate in the direction of the axis C of the rotary shaft 9, and a compression chamber is formed by the cylinder chamber 10 and the piston 11.

The valve plate 6 includes a suction valve mechanism that opens and closes the suction hole and the suction hole that communicates the cylinder chamber 10 and the suction chamber 7, and a discharge valve that opens and closes the discharge hole and the discharge hole that communicates the cylinder chamber 10 and the discharge chamber 8. Mechanism.
When the volume of the compression chamber increases due to the movement of the piston 11, the refrigerant gas G is sucked into the compression chamber from the suction chamber 7 through the suction hole and the suction valve mechanism. On the other hand, when the volume of the compression chamber decreases due to the movement of the piston 11, the refrigerant gas G in the compression chamber is compressed, and the refrigerant gas G compressed to a high pressure is discharged into the discharge chamber 8 through the discharge hole and the discharge valve mechanism. .

The crank chamber 5 is provided with a reciprocating motion conversion mechanism that converts the rotation of the rotating shaft 9 into the reciprocating motion of the piston 11. The reciprocating motion conversion mechanism includes a lug plate 12, a sleeve 13, a journal 14, a swash plate 20, a connecting plate 15, and a pair of piston shoes 16.
Further, inside the crank chamber 5, a lubricating oil R that lubricates the sliding portion is stored.

The lug plate 12 is fixed to the rotary shaft 9 and is disposed on the inner wall surface inside the front head 2 via a thrust bearing 17.
The sleeve 13 is attached to the rotary shaft 9 so as to be movable in the direction of the axis C.
The journal 14 is connected to the sleeve 13 by a pivot pin 18. Therefore, the journal 14 can be rotated around the pivot pin 18 and the inclination of the rotation shaft 9 with respect to the direction of the axis C can be changed.

The lug plate 12 and the journal 14 are connected via pins 19 a and 19 b and a connecting plate 15. Thereby, the journal 14 also rotates integrally with the rotating shaft 9 together with the lug plate 12 via the connecting plate 15.
The connecting plate 15 is rotatable about the pins 19a and 19b, and can take a rotating posture corresponding to a change in the inclination of the journal 14.

  The swash plate 20 is fixed to the journal 14, whereby the swash plate 20 rotates integrally with the rotating shaft 9 and the inclination of the rotating shaft 9 with respect to the axis C direction can be changed according to the inclination of the journal 14. Yes. The swash plate 20 is inclined with respect to the direction orthogonal to the axis C direction of the rotating shaft 9 in the entire range in which the inclination can be changed (in the range in which the inclination can be changed, the swash plate 20 is orthogonal to the axis C direction). Never become posture).

The pair of piston shoes 16 are each formed in a hemispherical shape, and are slidably accommodated in a spherical accommodating portion 11 a formed on the rear side of the piston 11.
And it arrange | positions so that the swash plate 20 may be pinched | interposed between a pair of piston shoes 16. FIG.
Since the piston shoe 16 does not rotate, the swash plate 20 rotates with the rotary shaft 9 while sliding between the piston shoes 16 and 16 contacting the surfaces 20a and 20b of the swash plate 20, respectively.

Since the swash plate 20 is inclined with respect to the axis C direction of the rotation shaft 9, when the swash plate 20 rotates, a portion (sliding portion) that contacts the swash plate 20 corresponding to each piston shoe 16 is a shaft. Move in the direction of heart C. Each piston shoe 16 moves in the direction of the axis C following the sliding portion, whereby each piston 11 reciprocates in the cylinder chamber 10 along the direction of the axis C.
As the piston 11 reciprocates, the volume of the compression chamber changes, and the above-described suction, compression, and discharge of the refrigerant gas G are performed.

Next, a mechanism for changing the capacity of the compressor 100 will be described.
The swash plate 20 is configured so that the sleeve 13 moves in the direction of the axis C against the elastic force of the return spring 31 or the destroke spring 32 provided along the rotation shaft 9, so that the inclination angle (the rotation shaft 9 The angle of inclination with respect to a direction orthogonal to the direction of the axis C of the axis changes.
Here, the crank chamber 5 and the suction chamber 7 are always in communication with each other through an extraction passage, the crank chamber 5 and the discharge chamber 8 are in communication with each other through an air supply passage, and the air supply passage has a control for controlling opening and closing of the air supply passage. A valve 33 is provided.

When the supply passage is opened by the control valve 33, the high-pressure refrigerant gas G flows from the discharge chamber 8 through the supply passage into the crank chamber 5 and the pressure inside the crank chamber 5 increases. When the pressure inside the crank chamber 5 rises, the sleeve 13 moves in a direction approaching the cylinder block 1 against the elastic force of the return spring 31, and the inclination angle of the swash plate 20 becomes small.
Thereby, the stroke amount which the piston 11 reciprocates becomes small, and the discharge amount of the refrigerant gas G discharged from the compression chamber decreases.

On the other hand, when the supply passage is closed by the control valve 33, the high-pressure refrigerant gas G does not flow into the crank chamber 5, and the high-pressure refrigerant gas G in the crank chamber 5 passes through the extraction passage to the suction chamber 7. As a result, the pressure in the crank chamber 5 approaches the pressure in the suction chamber 7, the sleeve 13 moves away from the cylinder block 1 against the elastic force of the destroke spring 32, and the inclination of the swash plate 20 is reduced. The angle increases. And the stroke amount which the piston 11 reciprocates increases, and the discharge amount of the refrigerant gas G discharged from the compression chamber increases.
Therefore, the capacity (discharge amount) of the compressor 100 can be changed by controlling the opening and closing of the supply passage by the control valve 33.

<Detailed configuration of swash plate>
The swash plate 20 is arranged so that at least the outer peripheral portion in the radial direction centered on the axis C of the rotating shaft 9 is immersed in the lubricating oil R accumulated in the crank chamber 5.
2A and 2B are schematic views showing the detailed configuration of the swash plate 20, wherein FIG. 2A is a view seen in the direction of the axis C, and FIG. 2B is a side view taken along arrow B in FIG. In FIG. 2B, the swash plate 20 is described in a posture orthogonal to the axial center C direction (the horizontal direction in the figure), but this is merely a convenience for ease of description. Actually, as described above, the swash plate 20 is provided in a posture inclined with respect to a direction orthogonal to the direction of the axis C. Hereinafter, the same description is omitted.

As shown in FIG. 2A, a plurality of passages 21 are formed in the swash plate 20 radially. In this example, eight passages 21 are formed. The passages 21 are formed at equiangular intervals around the axis C.
The passage 21 passes through the outer peripheral portion 20C where the lubricating oil R is immersed and the portions 20A, 20B of the respective surfaces 20a, 20b with which the piston shoe 16 contacts. The outer peripheral portion 20C is the outer peripheral surface 20c of the swash plate 20 in this example.

The passage 21 is a tunnel-like space formed inside the swash plate 20, and the first passage 21a shown in FIG. 2 (A) and the second passage 21b shown in FIG. 2 (B) are connected. Is formed. The first passage 21a and the second passage 21b are each linear.
The first passage 21a extends from the outer peripheral surface 20c to the end 20e before the inner peripheral surface 20d fixed to the journal 14.

The opening 21c in the outer peripheral surface 20c of the first passage 21a is located on the front side in the rotation direction M of the swash plate 20 with respect to the end 20e in the circumferential direction. That is, the first passage 21 a is inclined with respect to the radial direction of the swash plate 20 in a direction in which the opening 21 c is closer to the front side in the rotational direction.
An inclination angle (hereinafter referred to as an inclination angle) θ of the first passage 21a with respect to the radial direction is set in a range of 25 to 55 [degrees]. In addition, the inclination angle θ is not limited to this angle range, and may be greater than 0 [degrees].

The second passage 21 b extends in the thickness direction of the swash plate 20 and penetrates over both surfaces 20 a and 20 b of the swash plate 20. Openings 21d and 21e in the respective surfaces 20a and 20b of the second passage 21b are formed in portions 20A and 20B where the piston shoe 16 contacts.
The second passage 21b passes through the end 20e of the first passage 21a, and the first passage 21a and the second passage 21b are connected at the end 20e.

2A is the locus of the innermost circumference of the portions 20A and 20B that are in contact with the piston shoe 16, and the alternate long and two short dashes line is the locus of the center of the portions 20A and 20B that are in contact with the piston shoe 16.
The openings 21d and 21e on both surfaces 20a and 20b of the second passage 21b are formed on the innermost track of the portions 20A and 20B that are in contact with the piston shoe 16 shown by a two-dot chain line in FIG. .

In the compressor 100 having the swash plate 20 with the passage 21 formed in this manner, the passage 21 in which the lubricating oil R accumulated in the bottom of the crank chamber 5 is immersed in the lubricating oil R as the swash plate 20 rotates. Is introduced into the first passage 21a from the opening 21c in the outer peripheral surface 20c.
The introduction of the lubricating oil R into the first passage 21a is realized by the inclined first passage 21a scooping up the lubricating oil R.

The lubricating oil R introduced into the first passage 21a flows into the second passage 21b from the terminal end 20e as the posture of the first passage 21a approaches horizontal due to the rotation of the swash plate 20. Then, while the rotation of the swash plate 20 further proceeds, the lubricating oil R flowing into the second passage 21b is discharged from the openings 21d and 21e in the respective surfaces 20a and 20b.
The lubricating oil R discharged from the opening 21d is diffused outward by the centrifugal force generated by the rotation of the swash plate 20, for example, along the surface 20a where the opening 21d is formed.
Similarly, the lubricating oil R discharged from the opening 21e is diffused outward in the radial direction through, for example, the surface 20b where the opening 21e is formed.

As a result, the lubricating oil R is supplied to the portions 20A and 20B that are in contact with the piston shoes 16 located on the outer side in the radial direction from the openings 21d and 21e.
In the compressor 100, even when the amount of the lubricating oil R accumulated in the crank chamber 5 is small, at least the amount of oil that the opening 21 c in the outer peripheral surface 20 c of the passage 21 formed in the swash plate 20 is immersed. If there is, the lubricating oil R can be supplied to the portions 20A, 20B with which the piston shoe 16 contacts.

As described above, according to the compressor 100 of the present embodiment, the lubricating oil R is supplied to the portions 20A and 20B with which the piston shoe 16 contacts within a short time after the compressor 100 is started and the swash plate 20 starts to rotate. be able to.
Since the passage 21 is a tunnel-like space formed inside the swash plate 20, the lubricating oil R introduced into the passage 21 from the opening 21c can be supplied to the openings 21d and 21e without waste. .

[Modification]
FIG. 3 is a view corresponding to FIG. 2A, showing an example in which the opening 21 c in the outer peripheral surface 20 c of the passage 21 shown in FIG. 2 is enlarged to the front side in the rotation direction M.
The passage 21 of the swash plate 20 in the compressor 100 of Embodiment 1 described above preferably has an enlarged area of the opening 21c in the outer peripheral surface 20c.
That is, as shown in FIG. 3, the swash plate 20 is formed with a notch 20g on the front side in the rotational direction M in the peripheral portion of the opening 21c on the outer peripheral surface 20c of the first passage 21a, thereby reducing the area of the opening 21c. It expands to the front side in the rotational direction M.

The first passage 21a formed with the notches 21g in this manner introduces more lubricating oil R into the first passage 21a when the swash plate 20 rotates in the rotational direction M and the opening 21c is immersed in the lubricating oil R. More lubricating oil R can be supplied to the portions 20A and 20B with which the piston shoe 16 contacts.
The notch 21g is not limited to the front side in the rotation direction M, and may be provided in the thickness direction of the swash plate 20 (left-right direction in FIG. 2B) to enlarge the area of the opening 21c in the outer peripheral surface 20c. In this case as well, more lubricating oil R can be introduced into the first passage 21a.

Further, the opening 21c may be partially closed by a wedge-shaped convex portion 21f protruding rearward in the rotational direction M and projecting forward in the rotational direction M. Accordingly, when the swash plate 20 rotates in the rotation direction M and the opening 21c is immersed in the lubricating oil R, the wedge-shaped convex portion 21f easily scoops the lubricating oil R in contact with the opening 21c, and more lubrication is performed. Oil R can be introduced into the first passage 21a.
The wedge-shaped convex portion 21f is joined to the swash plate 20 after the first passage 21a is formed.

The first embodiment is an example in which eight passages 21 are formed. However, the swash plate type gas compressor according to the present invention is not limited to this example, and at least one passage is formed. It only has to be done.
In addition, it is preferable to set the number of the passages 21 to the same number as the number of the pistons 11 or an integer multiple of 2 or more of the number of the pistons 11. Corresponding to the number of sliding portions (contact portions) between the swash plate 20 and the piston shoe 16, the passages 21 are formed so that the timing at which the lubricating oil R is supplied to each sliding portion can be made uniform. it can.

[Embodiment 2]
4A and 4B are schematic views showing a swash plate 40 having a passage 41 formed by a single linear space. FIG. 4A is a view seen in the direction of the axis C, and FIG. 4B is a view in FIG. The side view by arrow D is shown, respectively.
The swash plate 20 in the compressor 100 according to the first embodiment has a passage 21 formed by connecting a first passage 21a and a second passage 21b. However, the passage in the swash plate type gas compressor according to the present invention is not limited to that of the first embodiment.

That is, as the swash plate type gas compressor according to the present invention, in the compressor 100 of the embodiment shown in FIG. 1, the swash plate 40 shown in FIG. You can also
The swash plate 40 shown in FIG. 4 is formed by forming a single linear passage 41 from the outer peripheral surface 40c of the swash plate 40 to the portions 40A and 40B where the piston shoes 16 are in contact with each of the surfaces 40a and 40b. .
Each passage 41 is inclined at an inclination angle θ with respect to the radial direction, with the opening 41c being closer to the front side in the rotational direction M than the opening 41d or the opening 41e, like the passage 21.

Similar to the passage 21 in the first embodiment, these passages 41 are opened by the rotation of the swash plate 40, and the openings 41d and 41e of the passage 41 in the portions 40A and 40B where the piston shoe 16 comes into contact with the opening 41c of the passage 41 on the outer peripheral surface 40c. Until then, the lubricating oil R can be supplied in a short time.
In addition, unlike the passage 21, the passage 41 is formed in a single straight line, so that the production becomes easy and the production cost can be reduced.

In the example shown in FIG. 4, each passage 41 communicates only from one opening 41c on the outer peripheral surface 40c to one surface 40a or the other surface 40b, but from each opening 41c on the outer peripheral surface 40c. The passage 41 extending to the one surface 40a and the passage 41 extending to the other surface 40b may be formed. That is, two passages 41 and 41 may be formed for one opening 41c.
In the example shown in FIG. 4, the passage 41 extending to one surface 40a and the passage 41 extending to the other surface 40b are alternately formed in the circumferential direction, but extend to one surface 40a. The passages 41 and the passages 41 extending to the other surface 40b may not be formed alternately in the circumferential direction.

[Embodiment 3]
FIG. 5 is a schematic view showing a swash plate 50 in which a groove passage 51 is formed on one surface 50a and a groove passage 52 is formed on the other surface 50b, and (A) is viewed in the direction of the axis C. (B) and (B) respectively show the side view by the arrow E in (A).
The swash plates 20 and 40 in the compressor 100 of the first and second embodiments are such that the passages 21 and 41 are formed in a tunnel shape passing through the inside of the swash plates 20 and 40. The passage in the gas compressor is not limited to these forms.

That is, as the swash plate type gas compressor according to the present invention, in the compressor 100 of the embodiment shown in FIG. 1, the swash plate 50 shown in FIG. You can also
The swash plate 50 shown in FIG. 5 has passages 51 and 52 that lead from the outer peripheral surface 50c of the swash plate 50 to the portions 50A and 50B where the piston shoes 16 are in contact with the surfaces 50a and 50b. It is formed as a space.

Each of the passages 51 and 52 is an outer peripheral portion of each of the surfaces 50a and 50b (it does not have to be a portion corresponding to the outer peripheral surface 50c of the swash plate 50, and may be an outer portion that is immersed in the lubricating oil R) 51c. To the openings 51d and 52d corresponding to the portions 50A and 50B with which the piston shoe 16 contacts, respectively, are formed on the respective surfaces 50a and 50b.
Each passage 51 is inclined at an inclination angle θ with respect to the radial direction, with the openings 51c and 52c being closer to the front side in the rotational direction M than the opening 51d or the opening 52d, like the passages 21 and 41.

In the same manner as the passage 21 in the first embodiment and the passage 41 in the second embodiment, the piston shoes 16 come into contact with the passages 51 and 52 from the openings 51c and 52c of the passages 51 and 52 in the outer peripheral portion by rotation of the swash plate 50. The lubricating oil R can be supplied in a short time to the openings 51d and 52d of the passages 51 and 52 in the portions 50A and 50B.
Note that the passages 51 and 52 that are groove-like spaces are different from the tunnel-like spaces, and part of the peripheral surfaces of the passages 51 and 52 are always open, so that the lubricating oil introduced into the passages 51 and 52 A part of R tends to flow out to the surfaces 50a and 50b in the middle of reaching the openings 51d and 52d.
However, on the other hand, there is an effect that the lubricating oil R that has flowed out to the surfaces 50a and 50b in this way easily diffuses onto the surfaces 50a and 50b.

  In the swash plate 50 according to the third embodiment, the openings 51c and 52c in the outer peripheral portion may be enlarged to the front side in the rotation direction M, similarly to the opening 21c shown in FIG. In this case, more lubricating oil R can be introduced into the passages 51 and 52, and more lubricating oil R can be supplied to the portions 50A and 50B with which the piston shoe 16 contacts.

[Modification]
FIG. 6 shows a plurality of radial passages 61 and 62 corresponding to the radially extending passages 51 and 52 shown in FIG. 5, and their central ends (passages in the portions 60 </ b> A and 60 </ b> B with which the piston shoe 16 contacts). A swash plate 60 having a structure connected to annular passages 63 and 64 at openings 61d and 62d) of 61 and 62 is shown.

The swash plate 60 thus configured is also an embodiment of a swash plate in the swash plate type gas compressor according to the present invention.
Then, according to the swash plate 60, the lubricating oil R introduced into the passages 61 and 62 is guided to the openings 61d and 62d of the passages 61 and 62 in the portions 60A and 60B where the piston shoe 16 is in contact, and from there, each surface 60a, Although part of the lubricating oil R flows to the annular passages 63 and 64, it is temporarily held in these passages 63 and 64.

Since the lubricating oil R held in the passages 63 and 64 is gradually discharged from the passages 63 and 64 gradually by centrifugal force while the swash plate 60 is rotating, the surfaces 60a and 60b of the swash plate 60 are discharged. It is possible to adjust the amount of the lubricating oil R that is diffused.
The passage 63 does not need to be connected to all the passages 61, and may be any as long as it forms an oil reservoir on the side of the opening 61 d of the passage 61 in the portion 60 </ b> A with which the piston shoe 16 contacts. The passages 64 do not need to connect all the passages 62 as long as they form an oil reservoir on the side of the opening 62d of the passage 62 in the portion 60B where the piston shoe 16 contacts.

The compressor 100 of each embodiment described above is a variable capacity type gas compressor, but the swash plate type gas compressor according to the present invention is not limited to a variable capacity type gas compressor, and is fixed. It may be a capacity type gas compressor.
In the case of a fixed capacity type gas compressor, a double-headed type that performs suction, compression, and discharge on both sides of a reciprocating piston may be used, or suction, compression, and discharge are performed only on one side of a reciprocating piston. A single-headed type may be used.

9 Rotating shaft 16 Piston shoe 20 Swash plates 20A, 20B Parts 20a, 20b surface 20c outer peripheral surface 20e end 21 passage 21a first passage 21b second passages 21c, 21d, 21e opening 100 compressor C shaft center G refrigerant gas M Rotation direction R Lubricating oil θ Inclination angle

Claims (5)

At least an outer peripheral portion in a radial direction centered on the shaft center is fixed to the lubricating oil accumulated in the crank chamber in a posture inclined with respect to the shaft center of the rotation shaft rotating with respect to the crank chamber. A swashplate arranged to immerse,
A piston shoe that is provided on a piston that reciprocates along the axis, and that slides between the rotating swash plate in contact with the surface of the swash plate;
The swash plate has a passage that passes through an outer peripheral portion and a portion of the surface where the piston shoe contacts, and the passage has an opening in the outer peripheral portion on the front side in the rotational direction with respect to the radial direction of the swash plate. A swash plate type gas compressor inclined in the direction of the approach.   2. The swash plate type gas compressor according to claim 1, wherein a notch for enlarging the opening is formed in a front portion in a rotation direction of the rotating shaft among peripheral portions of the outer peripheral portion of the swash plate.   The swash plate type gas compressor according to claim 1, wherein the passage is a space formed in a tunnel shape inside the swash plate.   The swash plate type gas compressor according to claim 1, wherein the passage is a space formed in a groove shape on a surface of the swash plate. A plurality of pistons provided around the rotation shaft, and reciprocating along the direction of the axis;
The swash plate type gas compressor according to any one of claims 1 to 4, wherein the passage is formed by a number that is a multiple of 1 or more of the number of the cylinders.