JP4392638B2 - Variable capacity swash plate compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a variable displacement swash plate compressor in which a stroke amount of a piston changes in accordance with a change in an inclination angle of a swash plate and a discharge capacity changes.
[0002]
[Prior art]
FIG. 8 is a longitudinal sectional view showing a maximum discharge capacity state of a conventional variable capacity swash plate compressor.
[0003]
The variable capacity swash plate compressor is mounted on a cylinder block 101 in which a plurality of cylinder bores 106 are formed, a shaft 105 rotatably supported at the center of the cylinder block 101, and a slidable and tiltable shaft 105. The swash plate 110 is connected to the swash plate 110 via a pair of shoes 150 that relatively rotate on both end surfaces 110a and 110b of the swash plate 110. Piston 107 that linearly reciprocates in cylinder bore 106 as the engine rotates, discharge chamber 112 that stores refrigerant gas discharged from compression chamber 106a in cylinder bore 106, and gas introduction that introduces refrigerant gas in discharge chamber 112 to crank chamber 108 The gas introduction passage 157 is provided in the middle of the passage 157 and the gas introduction passage 157 according to the change in the heat load. And a pressure control valve 181 for adjusting the cross-sectional area.
[0004]
When the pressure in the crank chamber 108 changes, the inclination angle of the swash plate 110 changes according to the pressure change, and the stroke amount of the piston 107 changes. As a result, the discharge capacity changes.
[0005]
The high-pressure refrigerant gas from the discharge chamber 12 introduced into the crank chamber 108 via the pressure control valve 181 contains oil, and this oil slides between the shoe 150 and both end faces 110a and 110b of the swash plate 110. Then, the gas is ejected from the outlet side opening 157a of the gas introduction passage 157, and the sliding portion is lubricated.
[0006]
[Problems to be solved by the invention]
However, this compressor is liable to be poorly lubricated for the following reasons, and the sliding portion may be seized or worn, and it has been difficult to ensure sufficient durability.
[0007]
FIG. 9 is a diagram illustrating shoe lubrication.
[0008]
Since the conventional compressor has only one gas introduction passage 157, it is difficult to sufficiently supply oil to the swash plate 110, the shoe 150, and the sliding portion during one rotation of the swash plate 110.
[0009]
Further, as shown in FIG. 9, the region A (shaded portion) where the refrigerant gas is discharged from the outlet side opening 157a is disengaged from the shoe sliding region B on the one end surface 110a of the swash plate 110, and the shoe 150 and the swash plate Oil cannot be effectively supplied to the sliding portion with 110.
[0010]
Further, since the gas introduction passage 157 requires a predetermined cross-sectional area and has a relatively large diameter, the initial speed when the refrigerant gas is ejected (at the time of supply) is reduced, and the oil is shoeed over the entire circumference of the swash plate 110. It is difficult to reach the sliding area.
[0011]
The present invention has been made in view of such circumstances, and its problem is to improve the durability of the variable capacity swash plate compressor by supplying sufficient oil to the sliding portion between the shoe and the swash plate. That is.
[0012]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the invention according to claim 1 is a cylinder block in which a plurality of cylinder bores are formed, a shaft rotatably supported at the center of the cylinder block, and a slide and tilt on the shaft. The swash plate is connected to the swash plate through a pair of shoes that relatively rotate on both end surfaces of the swash plate, and a crank chamber that houses the swash plate, and as the swash plate rotates. A piston that linearly reciprocates in the cylinder bore, a discharge chamber that stores refrigerant gas discharged from a compression chamber in the cylinder bore, a gas introduction passage that guides the refrigerant gas in the discharge chamber to the crank chamber, and the gas introduction passage And a pressure control valve that adjusts the cross-sectional area of the gas introduction passage according to a change in thermal load, and an inclination angle of the swash plate according to a change in pressure in the crank chamber Instead, in the variable capacity swash plate type compressor stroke of the piston is changed, the downstream refrigerant gas in the pressure control valve at least one includes a gas introducing auxiliary passage leading to the crank chamber, the outlet of the gas introduction passage The side opening and the outlet side opening of the gas introduction auxiliary passage are inclined holes for guiding the refrigerant gas toward the sliding region of the shoe on one end face of the swash plate.
[0013]
The refrigerant gas that has flowed out of the gas introduction passage and the oblique introduction hole of the gas introduction auxiliary passage is supplied to the shoe sliding region on one end surface of the swash plate.
[0014]
According to a second aspect of the invention, in the variable capacity swash plate type compressor according to claim 1, wherein the oblique bore and characterized in that for guiding the refrigerant gas toward the rotation direction front side of the farthest shoe from the cylinder block To do.
[0015]
The refrigerant gas that has flowed out while being guided by the oblique holes is supplied to the front side in the rotational direction of the shoe farthest from the cylinder block.
[0016]
According to a third aspect of the present invention, in the variable capacity swash plate compressor according to the first aspect, the outlet side opening of the gas introduction passage and the outlet side opening of the gas introduction auxiliary passage are on one end surface of the swash plate. A guide means for guiding the refrigerant gas toward the sliding region of the shoe is provided.
[0017]
Refrigerant gas flowing out from the outlet side opening of the gas introduction passage and the outlet side opening of the gas introduction auxiliary passage is respectively guided by the guide means and supplied to the sliding region of the shoe on the one end face of the swash plate.
[0018]
According to a fourth aspect of the present invention, in the variable displacement swash plate compressor according to the third aspect , the guide means guides the refrigerant gas toward the front side in the rotational direction of the shoe farthest from the cylinder block. It is characterized by.
[0019]
The refrigerant gas flowing out from the outlet side opening of the gas introduction passage and the outlet side opening of the gas introduction auxiliary passage is guided by the guide means and supplied to the front side in the rotational direction of the shoe farthest from the cylinder block.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0021]
1 is a longitudinal sectional view of a variable capacity swash plate compressor according to an embodiment of the present invention, FIG. 2 is an end view of a cylinder block as viewed from the front side, and FIG. 3 is a sectional view taken along the line III-III in FIG. FIG. 4 is an end view of the cylinder block as seen from the rear side.
[0022]
A rear head 3 is fixed to one end surface of the cylinder block 1 of the variable capacity swash plate compressor via a valve plate 2 and a front head 4 is fixed to the other end surface.
[0022]
The cylinder block 1 is provided with a plurality of cylinder bores 6 at predetermined intervals in the circumferential direction around the shaft 5. Pistons 7 are slidably accommodated in the cylinder bores 6, respectively.
[0023]
A crank chamber 8 is formed in the front head 4, and a swash plate 10 is accommodated in the crank chamber 8. The swash plate 10 is slidably attached to the shaft 5 via a hinge ball 9.
[0024]
The swash plate 10 is connected to the piston 7 via a shoe 50. The shoe 50 is supported by support recesses 7a and 7b of the piston 7 so as to be rotatable relative to both end faces 10a and 10b of the swash plate 10.
[0025]
The rear head 3 is formed with a discharge chamber 12 and a suction chamber 13 positioned around the discharge chamber 12.
[0026]
The discharge chamber 12 and the crank chamber 8 communicate with each other through a gas introduction passage 57. A control valve (pressure control valve) 81 is provided in the middle of the gas introduction passage 57.
[0027]
A part of the gas introduction passage 57, that is, a part from the control valve (pressure control valve) 81 to the crank chamber 8 is constituted by a series of communication holes formed in the rear head 3, the valve plate 2 and the cylinder block 1.
[0028]
A groove 57b constituting a part of the communication hole is formed on the rear side end face of the cylinder block 1.
[0029]
The cylinder block 1 is formed with a passage (gas introduction auxiliary passage) 57c extending from the groove 57b to the crank chamber 8.
[0030]
In the outlet side opening 57 a of the gas introduction passage 57, an oblique hole 60 a that guides the refrigerant gas toward the sliding region of the shoe 50 on the one end face 10 a of the swash plate 10 is formed.
[0031]
In the outlet side opening 57d of the passage 57c, an oblique hole 60b for guiding the refrigerant gas toward the sliding region of the shoe 50 on the one end face 10a of the swash plate 10 is formed.
[0032]
The oblique holes 60 a and 60 b are formed so as to be oblique to the shaft 5 and away from the shaft 5 so as to guide the refrigerant gas to the front side in the rotational direction of the shoe 50 farthest from the cylinder block 1.
[0033]
When the thermal load is large, the cross-sectional area of the passage 57 is reduced by energizing a solenoid (not shown) of the control valve 81, and when the thermal load is small, the cross-sectional area of the passage 57 is increased by stopping energization of the solenoid.
[0034]
The suction chamber 13 and the crank chamber 8 communicate with each other via a passage 58 provided in the cylinder block 1.
[0035]
The valve plate 2 is provided with a discharge port 16 for communicating the cylinder bore 6 and the discharge chamber 12 and a suction port 15 for communicating the cylinder bore 6 and the suction chamber 13 at predetermined intervals in the circumferential direction.
[0036]
The discharge port 16 is opened and closed by a discharge valve 17, and the discharge valve 17 is fixed to a rear head side end face of the valve plate 2 by a bolt 19 together with a valve presser 18.
[0037]
The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is disposed between the valve plate 2 and the cylinder block 1.
[0038]
A rear side end portion of the shaft 5 is rotatably supported by a radial bearing 24 and a thrust bearing 25, and a front side end portion of the shaft 5 is rotatably supported by a radial bearing 26.
[0039]
A thrust flange 40 is fixed to the front side of the shaft 5. The thrust flange 40 is supported on the inner wall surface of the front head 4 via a thrust bearing 33.
[0040]
A hinge ball 9 that supports the swash plate 10 is slidably mounted on the shaft 5.
[0041]
The thrust flange 40 and the swash plate 10 are connected via a link mechanism 41 described later, and the rotation of the shaft 5 is transmitted from the thrust flange 40 to the swash plate 10 via the link mechanism 41.
[0042]
The link mechanism 41 includes a protrusion 45 provided on the thrust flange 40, a linear guide groove 46 provided on the protrusion 45, and a pin 10 d provided on the bracket 10 c of the swash plate 10. .
[0043]
The longitudinal axis of the guide groove 46 is inclined at a predetermined angle with respect to the surface 40a where the thrust flange 40 and the thrust bearing 33 contact. The spherical portion 10 d is slidably fitted in the guide groove 46.
[0044]
Next, the operation of this variable capacity swash plate compressor will be described.
[0045]
FIG. 5 is a diagram for explaining the lubrication of the shoe.
[0046]
When the rotational power of the in-vehicle engine is transmitted to the shaft 5, the rotational force of the shaft 5 is transmitted to the swash plate 10 through the thrust flange 40 and the hinge mechanism 41, and the swash plate 10 rotates.
[0047]
Since the shoe 50 relatively rotates on the end faces 10 a and 10 b of the swash plate 10 by the rotation of the swash plate 10, the rotational force from the swash plate 10 is converted into the linear reciprocating motion of the piston 7.
[0048]
The piston 7 reciprocates in the cylinder bore 6, and as a result, the volume of the compression chamber 6 a in the cylinder bore 6 changes. By this volume change, refrigerant gas is sucked, compressed, and discharged in sequence, and the swash plate 10 is inclined at an inclination angle. A corresponding volume of refrigerant gas is discharged.
[0049]
During suction, the suction valve 21 is opened, low pressure refrigerant is sucked from the suction chamber 13 into the compression chamber 6a in the cylinder bore 6, and during discharge, the discharge valve 17 is opened, and high pressure refrigerant gas flows from the compression chamber 6a to the discharge chamber 12. Discharged.
[0050]
When the thermal load is reduced, energization to the solenoid of the control valve 81 is stopped and the cross-sectional area of the gas introduction passage 57 is increased.
[0051]
Therefore, high-pressure refrigerant gas flows from the discharge chamber 12 into the crank chamber 8 through the gas introduction passage 57 and the passage 57c, and the pressure in the crank chamber 8 increases.
[0052]
The force applied to the bottom surface of the piston 7 during the compression process is increased, and the sum of the forces applied to the bottom surface of the piston 7 exceeds the sum of the forces applied to the top surface of the piston. As a result, the inclination angle of the swash plate 10 is reduced. Become.
[0053]
On the other hand, when the thermal load increases, the cross-sectional area of the gas introduction passage 57 decreases due to energization of the solenoid of the control valve 81.
[0054]
Therefore, inflow of high-pressure refrigerant gas from the discharge chamber 12 to the crank chamber 8 is suppressed, and the pressure in the crank chamber 8 is reduced.
[0055]
Then, the force applied to the bottom surface of the piston 7 during the compression process is reduced, and the total force applied to the bottom surface of the piston 7 is less than the total force applied to the top surface of the piston. As a result, the inclination angle of the swash plate 10 is increased. Become.
[0056]
During one rotation of the swash plate 10, the high-pressure refrigerant gas flowing out from the discharge chamber 12 to the crank chamber 8 through the oblique holes 60 a of the gas introduction passage 57 and the oblique holes 60 b of the passage 57 c is shown in the region A (indicated by the oblique lines in FIG. 5). To the indicated area). This area A is included in the sliding area B of the shoe 50 on the one end face 10 a of the swash plate 10.
[0057]
According to the variable capacity swash plate compressor of this embodiment, oil contained in the refrigerant gas is applied to the sliding surface between the shoe 50 and the swash plate 10 over the entire circumference of the swash plate during one rotation of the swash plate 10. Since it is supplied, the lubricity of the sliding surface between the shoe 50 and the swash plate 10 is dramatically improved, seizure due to insufficient oil can be prevented, wear can be reduced, and durability is improved.
[0058]
FIG. 6 is a partial sectional view showing a modification of the guide means.
[0059]
In this modification, a hole 60a is not formed as a guide means in the outlet side opening 57a of the gas introduction passage 57, but in the vicinity of the outlet side opening 57a of the gas introduction passage 57 and on the front side end face of the cylinder block 1. This is different from the above embodiment in that an inclined plate 70 for guiding the refrigerant gas is provided on the front side in the rotation direction of the shoe 50 farthest from the block 1.
[0060]
The inclined plate 70 is provided so as to be inclined with respect to the shaft 5 (see FIG. 1) and gradually away from the shaft 5.
[0061]
According to this modification, the same effects as those of the above embodiment can be obtained.
[0062]
FIG. 7 is a partial sectional view showing another modification of the guide means.
[0063]
In this modification, the hole 60a is not formed as a guide means in the outlet side opening 57a of the gas introduction passage 57, but in the rotation direction front side of the shoe 50 farthest from the cylinder block 1 in the outlet side opening 57a of the gas introduction passage 57. The difference from the above embodiment is that a pipe 80 for guiding the refrigerant gas is provided.
[0064]
One end 80a of the pipe 80 is inserted into the outlet side opening 57a, and the other end 80b is bent obliquely with respect to the shaft 5 (see FIG. 1) and gradually away from the shaft 5.
[0065]
According to this modification, the same effects as those of the above embodiment can be obtained.
[0066]
In the above embodiment, the case where one passage 57c is formed has been described. However, the number of the passages 57c is not limited to one, and may be two or more.
[0067]
Further, the inclined plate 70 and the pipe 80 are provided in the outlet side opening 57a of the gas introduction passage 57, but the present invention is not limited to this, and may be provided in the outlet side opening 57d of the passage 57c.
[0068]
Further, in each of the above embodiments, the case where only the oblique holes 60a and 60b are formed or only the inclined plate 70 and the pipe 80 are provided for one compressor has been described. For example, a conventional gas inlet passage outlet is provided. The inclined hole, the inclined plate 70 and the pipe may be arbitrarily combined, such as providing an inclined plate or a pipe in the side opening and forming an inclined hole in the outlet side opening of the passage.
【The invention's effect】
[0069]
As described above, according to the variable capacity swash plate compressor of the first or third aspect of the invention, the oil contained in the refrigerant gas over the entire circumference of the swash plate during one rotation of the swash plate Supplied to the sliding surface with the swash plate, reliable lubrication can be performed, seizure due to lack of oil can be prevented, wear can be reduced, and durability is improved.
[0071]
According to the variable capacity swash plate compressor of the invention described in claim 2 or 4 , the oil supply does not come off from the shoe sliding area on one end face of the swash plate, and the sliding portion between the shoe and the swash plate Oil can be supplied effectively.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a variable capacity swash plate compressor according to an embodiment of the present invention.
FIG. 2 is an end view of the cylinder block as viewed from the front side.
FIG. 3 is a cross-sectional view taken along the line II-II in FIG.
FIG. 4 is an end view of the cylinder block as viewed from the rear side.
FIG. 5 is a diagram illustrating shoe lubrication.
FIG. 6 is a partial sectional view showing a modification of the guide means.
FIG. 7 is a partial sectional view showing another modification of the guide means.
FIG. 8 is a longitudinal sectional view showing a maximum discharge capacity state of a conventional variable capacity swash plate compressor.
FIG. 9 is a diagram illustrating shoe lubrication.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Cylinder block 5 Shaft 6 Cylinder bore 6a Compression chamber 7 Piston 8 Crank chamber 10 Swash plate 12 Discharge chamber 50 Shoe 57 Gas introduction passage 57a Outlet side opening 60 Diagonal hole 81 Control valve (pressure adjustment valve)
70 Inclined plate (guide means)
80 pipe (guide means)

Claims (4)

A cylinder block in which a plurality of cylinder bores are formed, a shaft rotatably supported at the center of the cylinder block, a swash plate that is slidably and tiltably attached to the shaft, and a crank that houses the swash plate A chamber, a piston coupled to the swash plate via a pair of shoes that rotate relatively on both end faces of the swash plate, and a linear reciprocating motion in the cylinder bore as the swash plate rotates, and a compression in the cylinder bore A discharge chamber for storing the refrigerant gas discharged from the chamber; a gas introduction passage for guiding the refrigerant gas in the discharge chamber to the crank chamber; and the gas according to a change in heat load, provided in the middle of the gas introduction passage. A pressure control valve for adjusting the cross-sectional area of the introduction passage, and the inclination angle of the swash plate changes according to the pressure change of the crank chamber, and the stroke amount of the piston changes. In a variation capacity swash plate type compressor, an outlet downstream of the refrigerant gas at least one includes a gas introducing auxiliary passage leading to the crank chamber, the gas introduction auxiliary passage and outlet opening of the gas inlet passage of the pressure control valve A variable capacity swash plate compressor characterized in that the side opening is an oblique hole for guiding refrigerant gas toward the sliding region of the shoe on one end face of the swash plate.   2. The variable capacity swash plate compressor according to claim 1, wherein the oblique hole guides the refrigerant gas toward the front side in the rotation direction of the shoe farthest from the cylinder block. Guide means for guiding the refrigerant gas toward the sliding region of the shoe on one end face of the swash plate is provided at the outlet side opening of the gas introduction passage and the outlet side opening of the gas introduction auxiliary passage. The variable capacity swash plate compressor according to claim 1 . 4. The variable capacity swash plate compressor according to claim 3 , wherein the guide means guides the refrigerant gas toward the front side in the rotational direction of the shoe farthest from the cylinder block.

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