JP4630801B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor.

  For example, a compressor disclosed in Patent Document 1 includes a cylinder block having a plurality of cylinder bores along the circumferential direction, a front housing joined to the front end surface of the cylinder block to form a crank chamber therein, and a rear of the cylinder block. A rear housing joined to the end face via a valve plate and forming a suction chamber and a discharge chamber therein.

  A central through hole as a bearing hole is formed in the cylinder block, and a drive shaft is supported by the central through hole via a bearing. A rotary swash plate that rotates integrally with the drive shaft is attached to the drive shaft. A piston is engaged with the rotary swash plate, and when the rotary swash plate rotates, the piston reciprocates within the cylinder bore. When the piston reciprocates, refrigerant is sucked into the cylinder bore from the suction chamber in the piston suction process, refrigerant gas is compressed in the cylinder bore in the piston compression stroke, and finally the compressed refrigerant is discharged into the discharge chamber. The

  The rotating swash plate is attached so as to be tiltable with respect to the drive shaft and slidable in the axial direction, and the tilt angle is changed depending on the slide position. When the inclination angle of the rotating swash plate is changed, the piston stroke changes, and the discharge capacity of the compressor changes.

This compressor communicates the crank chamber and the suction chamber, connects the crank chamber and the discharge chamber to the extraction passage for extracting the refrigerant gas from the crank chamber to the suction chamber, and supplies the refrigerant gas from the discharge chamber to the crank chamber. An air passage and a control valve provided in the middle of at least one of these passages are provided. By opening and closing the control valve, the pressure in the crank chamber can be adjusted, and the piston stroke (that is, the inclination angle of the rotary swash plate) is determined based on the differential pressure between the pressure in the crank chamber and the suction pressure in the cylinder bore. It has become.
JP-A-5-231309

  In this type of compressor, the lubricating oil is mixed in the refrigerant, whereby the lubricating oil is supplied to the sliding parts in the compressor.

  The blow-by gas from the cylinder bore (refrigerant gas and lubricating oil that leaks into the crank chamber from the gap between the cylinder bore and the piston during compression) always flows into the crank chamber, and rotation of swash plates, etc., occurs in the crank chamber. Since the refrigerant gas and the lubricating oil are stirred by the body, a relatively large amount of lubricating oil is supplied to the sliding parts in the crank chamber. However, it is difficult for lubricating oil to be supplied into the bearing hole, that is, to the bearing that supports the drive shaft.

  The present invention has been made based on such a conventional technique, and an object of the present invention is to provide a compressor capable of supplying a large amount of lubricating oil to a bearing that supports a drive shaft.

The compressor according to the first aspect of the present invention includes a suction chamber provided on the top dead center side of the cylinder bore via a suction valve mechanism, and a discharge chamber provided on the top dead center side of the cylinder bore via a discharge valve mechanism. A crankshaft provided on the bottom dead center side of the cylinder bore, a drive shaft pivotally supported via a bearing in a bearing hole communicating with the crank chamber, and rotatable in the crank chamber, the drive shaft A piston that reciprocates in the cylinder bore as the cylinder rotates, and an inlet of an extraction passage communicating the suction chamber and the crank chamber is opened on the outer periphery of the drive shaft, and the inlet of the extraction passage is And located in the bearing hole and on the bearing side of any component mounted on the drive shaft in the crank chamber, the bearing hole being recessed in the radial direction from the main body and the crank chamber side From A groove-shaped passage expanding portion extending toward the bearing side is provided .

According to a second aspect of the present invention, a cylinder block having a bearing hole and having a plurality of cylinder bores along the circumferential direction around the bearing hole is joined to a front end surface of the cylinder block to form a crank chamber therein. A front housing, a rear housing joined to a rear end surface of the cylinder block via a valve plate to form a suction chamber and a discharge chamber therein, and a rear end portion of the cylinder block through a bearing through a bearing hole. A drive shaft that is supported and rotatable within the crank chamber, and an outer periphery of the drive shaft has an opening of an extraction passage communicating the suction chamber and the crank chamber, and an inlet of the extraction passage is while positioned in the bearing bore is located in the bearing side than the part to be mounted on the drive shaft in the crank chamber, the bearing hole, Characterized in that from recessed from the body portion in a radial direction and the crank chamber side includes a passage enlarged portion of a groove shape extending toward the bearing side.

  A third aspect of the present invention is the compressor according to the first or second aspect, wherein the compressor is tiltable with respect to the drive shaft and slidable in the axial direction in the crank chamber, and is tilted according to a slide position. A swash plate having a variable angle and reciprocatingly moving the piston as the drive shaft rotates, and is mounted between the swash plate and the bearing on the outer periphery of the drive shaft. A return spring that urges in a separating direction, and an inlet of the extraction passage is provided closer to the bearing than the return spring.

A fourth aspect of the present invention is the compressor according to the first or second aspect , wherein the passage enlarged portion is provided above the main body portion, and an upper end surface of the passage enlarged portion is formed in the crank chamber. characterized in that it inclined downward toward the side on the bearing side.

According to the first and second aspects of the present invention, since the refrigerant gas flowing from the crank chamber to the suction chamber flows into the bearing hole from the crank chamber and flows in the vicinity of the bearing, the mist-like lubricating oil accompanying the refrigerant gas is supplied. More can be supplied to the bearing. Further, since the bearing hole is provided with a groove-shaped passage expanding portion that is recessed from the main body portion in the radial direction and extends from the crank chamber side toward the bearing side, more refrigerant gas can be circulated in the vicinity of the bearing. since it, to further improve lubricity of the bearing.

  According to the third aspect of the present invention, the effects of the first and second aspects of the present invention can be obtained even with a structure including a return spring that is disposed particularly close to the bearing.

According to the fourth aspect of the present invention, the passage enlargement portion is provided above the main body portion, and the passage enlargement portion is inclined downward from the crank chamber side toward the bearing side. The lubricating oil adhering to the inner peripheral surface flows along the inclination of the passage expanding portion by its own weight and is supplied to the bearing. Therefore, it is possible to supply many more lubricating oil to the bearing.

  Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to the drawings.

"Overall structure of compressor"
FIG. 1 is an overall cross-sectional view of the compressor, and FIG. 2 is a front view of the cylinder block as viewed from the direction of arrow II in FIG.

  The compressor 1 of this embodiment is a swash plate type variable capacity compressor as shown in FIG. The variable capacity compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3 (see FIG. 2) arranged at equal intervals in the circumferential direction, and a cylinder block 2 joined to a front end surface of the cylinder block 2. A front housing 4 that forms a crank chamber 5 therebetween, and a rear housing 6 that is joined to a rear end surface of the cylinder block 2 via a valve plate 9 to form a suction chamber 7 and a discharge chamber 8 are provided. The cylinder block 2, the front housing 4 and the rear housing 6 are fastened and fixed by a plurality of through bolts 13.

  The valve plate 9 includes a suction hole (not shown) that allows the cylinder bore 3 and the suction chamber 7 to communicate with each other, and a discharge hole 12 that allows the cylinder bore 3 and the discharge chamber 8 to communicate with each other.

  A suction valve mechanism (not shown) for opening and closing the suction hole 11 is provided on the cylinder block 2 side of the valve plate 9, while a discharge (not shown) for opening and closing the discharge hole 12 is provided on the rear housing 6 side of the valve plate 9. A valve mechanism is provided. A gasket (not shown) is interposed between the valve plate 9 and the rear housing 6 so that the airtightness of the suction chamber 7 and the discharge chamber 8 is maintained.

  The drive shaft 10 is pivotally supported via radial bearings 15 and 19 in the central through holes 14 and 18 serving as bearing holes at the center of the cylinder block 2 and the front housing 4, whereby the drive shaft 10 rotates in the crank chamber 5. It is free. A thrust bearing 20 is interposed between the front end surface of the lug drive 21 fixed to the drive shaft 10 and the inner wall surface of the front housing 4, and is fixed to the rear end opening of the central through hole 14 of the cylinder block 2. A thrust bearing 16 is interposed between the adjusted screw 17 and the rear end surface of the drive shaft 10.

  In the crank chamber 5, a lug drive 21 as a rotating member fixed to the drive shaft 10, a sleeve 22 slidably attached to the drive shaft 10, and a swash plate attached to the sleeve 22 so as to be tiltable. And a rotary swash plate 24. That is, the rotary swash plate 24 is mounted so as to be tiltable with respect to the drive shaft 10 and to be slidable in the axial direction of the drive shaft 10. In this example, the rotary swash plate 24 includes a journal 25 that is attached to the sleeve 22 so as to be tiltable and rotatable, and a swash plate body 26 fixed to a boss portion 25 a of the journal 25.

  A piston 29 is slidably accommodated in each cylinder bore 3, and this piston 29 is connected to the rotary swash plate 24 via a pair of hemispherical piston shoes 30, 30.

  A connecting mechanism 40 is interposed between the lug drive 21 as the rotating member and the rotating swash plate 24 as the swash plate. The connecting mechanism 40 allows the fluctuation of the tilt angle of the rotating swash plate 24 while allowing the change in the tilt angle. The rotational torque of the drive 21 can be transmitted to the rotary swash plate 24.

  The inclination angle of the rotary swash plate 24 decreases as the sleeve 22 moves closer to the cylinder block 2 against the return spring 52, while the inclination angle of the rotary swash plate 24 decreases, while the sleeve 22 resists the destroke spring 51. Thus, when it moves in the direction away from the cylinder block 2, the inclination angle of the rotary swash plate 24 increases. A reference numeral 53 in FIG. 1 is a return spring stopper that is engaged with an annular groove 54 provided between the sleeve 22 and the radial bearing 15 on the outer periphery of the drive shaft 10.

  When the drive shaft 10 rotates, the lug drive 21 rotates integrally with the drive shaft 10, and the rotation of the lug drive 21 is transmitted to the rotary swash plate 24 via the coupling mechanism 40. The rotation of the rotary swash plate 24 is converted into a reciprocating motion of the piston 29 via the pair of piston shoes 30, 30, and the piston 29 reciprocates in the cylinder bore 3. By the reciprocating motion of the piston 29, the refrigerant in the suction chamber 7 is sucked into the cylinder bore 3 through the suction hole 11 of the valve plate 9 and then compressed in the cylinder bore 3, and the compressed refrigerant is discharged into the discharge hole 12 of the valve plate 9. Through the discharge chamber 8.

"Control of variable capacity"
In order to change the discharge capacity of the refrigerant, the piston stroke is changed by changing the inclination angle of the rotary swash plate 24. More specifically, the piston stroke is changed by changing the tilt angle of the rotary swash plate 24 by the differential pressure (pressure balance) between the crank chamber pressure Pc on the rear surface side of the piston 29 and the suction chamber pressure Ps on the front surface side of the piston 29. Let Therefore, this variable displacement compressor, the pressure control mechanism is provided. The pressure control mechanism includes an extraction passage 60 (see FIG. 3) that communicates between the crank chamber 5 and the suction chamber 7, an air supply passage (not shown) that communicates between the crank chamber 5 and the discharge chamber 8, and this air supply. And a control valve 33 provided in the middle of the passage for controlling opening and closing of the air supply passage.

  When the air supply passage is opened by the control valve 33, a high-pressure refrigerant gas flows from the discharge chamber 8 through the air supply passage to the crank chamber 5, thereby increasing the pressure in the crank chamber 5. When the pressure in the crank chamber 5 increases, the inclination angle of the rotary swash plate 24 decreases while the sleeve 22 moves closer to the cylinder block 2 side, whereby the piston stroke becomes smaller and the discharge amount decreases.

  On the other hand, when the air supply passage is closed by the control valve 33, the refrigerant gas is always discharged into the suction chamber 7 into the crank chamber 5 through the extraction passage 60 (see FIG. 3). The pressure difference disappears and the pressure is equalized. Then, while the sleeve 22 moves away from the cylinder block 2, the inclination angle of the rotary swash plate 24 increases, the piston stroke increases, and the discharge amount increases.

"Cylinder block center through hole"
Next, the structure of the central through hole 14 of the cylinder block and its periphery will be described with reference to FIG.

  The central through-hole 14 of the cylinder block 2 of the present embodiment has an intermediate portion 14a provided at the middle portion in the longitudinal direction, and a front side that is provided closer to the front end surface side of the cylinder block 2 than the intermediate portion 14a and opens to the front end surface. The opening part 14b and the rear side opening part 14c provided in the rear-end surface side of the cylinder block 2 rather than the intermediate part 14a and opening to the said rear-end surface are provided.

  Of these three portions, the intermediate portion 14a is formed to have the smallest diameter, and the radial bearing 15 is disposed. In addition, a rear end portion of the return spring stopper 53 and the return spring 52 is disposed in the front opening portion 14b, and a thrust bearing 16 and an adjusting screw 17 are disposed in the rear opening portion 14c.

  In the present embodiment, the bleed passage 60 has a through passage 61 formed in the drive shaft 10, a rear opening 14 c that communicates with the through passage 61, and a passage formed in the valve plate 9 and communicates with the rear opening 14 c. And a passage 6 s formed in the rear housing 6 with one end communicating with the through hole 9 s and the other end communicating with the suction chamber 7.

  The through passage 61 formed in the drive shaft 10 has one end communicating with the crank chamber 5 and the other end communicating with the rear opening 14c. The through passage 61 has an axial passage 65 extending from the rear end to the front end side of the drive shaft 10 and a radial direction extending from the outer peripheral surface of the drive shaft 10 toward the axial passage 65 and communicating with the axial passage 65. And a passage 63. The radial passage 63 of the through passage 61 constitutes an inlet of the extraction passage 60 by communicating with the crank chamber 5 through the central through port 14.

  The inlet 63 of the extraction passage is located in the central through-hole 14 and is attached to any component (in this example, the lug drive 21, the destroke spring 51, the sleeve 22, The swash plate 24, the return spring 52, and the return spring stopper 53) are provided on the bearing 15 side. More specifically, the inlet 63 of the extraction passage opens to the outer peripheral surface of the drive shaft 10 between the return spring 52 and the bearing 15. Thereby, the refrigerant gas in the crank chamber 5 flows into the extraction passage 60 through the central through port 14. Therefore, since the refrigerant gas flowing from the crank chamber 5 toward the suction chamber 7 flows through the central through-hole 14 near the bearing 15, mist-like lubricating oil accompanying the refrigerant gas is supplied to the bearing 15. Become. Further, since the refrigerant gas flows in the vicinity of the bearing 15, it is possible to prevent the bearing 15 from being cooled and the bearing 15 from becoming excessively hot and deteriorating the lubricating performance of the lubricating oil. Thereby, the slidability of the bearing 15 can be further maintained high.

  Here, since a plurality of cylinder bores 3 are provided around the central through-hole 14 (see FIG. 2), the radial size of the central through-hole 14 is limited. That is, the size of the clearance between the inner peripheral surface of the front opening 14 b of the central through-hole 14 and the outer peripheral surface of the drive shaft 10 is limited. Therefore, there is a possibility that the amount of refrigerant gas that can flow between the inner peripheral surface of the front opening 14b of the central through-hole 14 and the outer peripheral surface of the drive shaft 10 may be limited. However, in this embodiment, the front opening 14b of the central through-hole 14 is recessed in the radial direction from the main body 66 having a circular cross section and extends in a groove shape from the crank chamber 5 side toward the bearing 15 side. 67 is formed. Therefore, more refrigerant gas can be circulated in the vicinity of the bearing 15, thereby further improving the lubricity of the bearing 15.

  The passage enlargement portion 67 is provided above the main body portion 66 and is inclined downward from the crank chamber 5 side toward the radial bearing 15 side.

"effect"
Then, enumerated the effect of the present embodiment.

  (1) According to this embodiment, the inlet 63 of the bleed passage 60 that communicates the suction chamber 7 and the crank chamber 5 is opened on the outer periphery of the drive shaft 10, and the inlet 63 of this bleed passage is the center as a bearing hole. Any component (in this example, lug drive 21, destroke spring 51, sleeve 22, rotary swash plate 24, return spring 52, return spring, which is located in the through-hole 14 and mounted on the drive shaft 10 in the crank chamber 5) Is provided closer to the bearing 15 than the stopper 53). Therefore, the refrigerant gas flowing from the crank chamber 5 toward the suction chamber 7 flows from the crank chamber 5 into the central through-hole 14 and flows in the vicinity of the bearing 15, so that mist-like lubricating oil accompanying the refrigerant gas is generated. More is supplied to the bearing 15.

  Moreover, the bearing 15 is cooled by the refrigerant gas flowing in the vicinity of the bearing 15. Thereby, it can prevent that the bearing 15 becomes high temperature too much and the lubrication performance of lubricating oil falls, and also the slidability of the bearing 15 can be maintained high.

  (2) According to the present embodiment, the crankshaft 5 is mounted so as to be tiltable with respect to the drive shaft 10 and slidable in the axial direction, and the tilt angle is variable depending on the slide position. Is mounted between the rotary swash plate 24 and the bearing 15 on the outer periphery of the drive shaft 10, and the rotary swash plate 24 is separated from the bearing 15. And a return spring 52 that is urged in the direction in which the bleed passage 60 is provided, and an inlet 63 of the extraction passage 60 is provided closer to the bearing 15 than the return spring 52.

  Therefore, even if the structure includes the return spring 52 that extends into the central through hole 14 and is particularly close to the bearing 15, the effect (1) can be obtained.

  (3) According to the present embodiment, the central through-hole 14 includes the groove-shaped passage expanding portion 67 that is recessed from the main body portion 66 in the radial direction and extends from the crank chamber 5 side toward the bearing 15 side. Therefore, more refrigerant gas can be circulated in the vicinity of the bearing 15. Thereby, the lubricity of the bearing 15 can be further improved.

  (4) According to the present embodiment, the passage expanding portion 67 is provided above the main body portion 66 and is inclined downward from the crank chamber 5 side toward the bearing 15 side. Therefore, the lubricating oil adhering to the inner peripheral surface of the passage expanding portion 67 immediately after the compressor stops flows along the inclination of the passage expanding portion 67 by its own weight and is supplied to the bearing 15. Therefore, more lubricating oil can be supplied to the bearing 15.

  Note that the present invention is not limited to the above-described embodiment.

  For example, although the swash type swash plate (rotary swash plate) is used in the above-described embodiment, a wobble type swash plate (non-rotating type swash plate) may be used in the present invention.

  In the above-described embodiment, the swash plate is attached to the drive shaft via a hinge ball as a sleeve, but the swash plate may be directly attached to the drive shaft without using a sleeve. Good.

  In the above-described embodiment, the member mounted on the drive shaft and closest to the bearing is the return spring and its stopper. However, other members mounted on the drive shaft may be closest to the bearing.

  Further, the present invention can be carried out in various other modes as long as they belong to the technical scope of the present invention.

FIG. 1 is a cross-sectional view of a compressor according to an embodiment of the present invention. FIG. 2 is a front view of the cylinder block as viewed from the direction of arrow II in FIG. FIG. 3 is an enlarged view of a main part of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Compressor 2 ... Cylinder block 3 ... Cylinder bore 4 ... Front housing 5 ... Crank chamber 6 ... Rear housing 7 ... Suction chamber 8 ... Discharge chamber 9 ... Valve plate 10 ... Drive shaft 14 ... Central through-hole (bearing hole)
15. Radial bearing (bearing)
22 ... sleeve (part to be mounted to the drive shaft)
24 ... swashplate (swash plate, parts to be mounted on the drive shaft)
29 ... Piston 51 ... destroke spring (part to be mounted to the drive shaft)
52 ... return spring (part to be mounted to the drive shaft)
53 ... stopper return spring (part to be mounted to the drive shaft)
60 ... bleed passage 63 ... radial passage (the inlet of the bleed passage)
66 ... body part 67 ... passage expansion part

Claims (4)

A suction chamber (7) provided via a suction valve mechanism on the top dead center side of the cylinder bore (3);
A discharge chamber (8) provided via a discharge valve mechanism on the top dead center side of the cylinder bore (3);
The crank chamber (5) provided on the bottom dead center side of the cylinder bore (3);
A drive shaft (10) rotatably supported in the crank chamber supported by a bearing hole (14) communicating with the crank chamber (5) via a bearing (15);
A piston (29) that reciprocates in the cylinder bore (3) as the drive shaft (10) rotates;
With
On the outer periphery of the drive shaft (10), an inlet (63) of an extraction passage (60) communicating with the suction chamber (7) and the crank chamber (5) is opened,
The inlet (63) of the bleed passage is located in the bearing hole (14) and in any part (21, 51, 22, 24) mounted on the drive shaft (10) in the crank chamber (5). , 52, 53) on the side of the bearing (15) , the bearing hole (14) is recessed in the radial direction from the main body (66), and the bearing (15) from the crank chamber (5) side. A compressor having a groove-shaped passage expanding portion (67) extending toward the) side . A cylinder block (2) having a bearing hole (14) and having a plurality of cylinder bores (3) around the bearing hole (14) in the circumferential direction;
A front housing (4) joined to the front end face of the cylinder block (2) to form a crank chamber (5) therein;
A rear housing (6) joined to the rear end surface of the cylinder block (2) via a valve plate (9) to form a suction chamber (7) and a discharge chamber (8) therein;
A drive shaft (10) whose rear end is pivotally supported via a bearing in the bearing hole (14) of the cylinder block (2) and rotatable in the crank chamber (5);
With
On the outer periphery of the drive shaft (10), an inlet (63) of an extraction passage (60) communicating with the suction chamber (7) and the crank chamber (5) is opened,
The inlet (63) of the bleed passage is located in the bearing hole (14) and in any part (21, 51, 22, 24) mounted on the drive shaft (10) in the crank chamber (5). , 52, 53) on the side of the bearing (15) , the bearing hole (14) is recessed in the radial direction from the main body (66), and the bearing (15) from the crank chamber (5) side. A compressor having a groove-shaped passage expanding portion (67) extending toward the) side . The compressor according to claim 1 or 2,
In the crank chamber (5), it is mounted so as to be tiltable with respect to the drive shaft (10) and slidable in the axial direction, and the tilt angle is variable depending on the slide position. As the drive shaft (10) rotates. swash plate for reciprocating the piston (29) and (24),
A return mounted on the outer periphery of the drive shaft (10) between the swash plate (24) and the bearing (15) and biasing the swash plate (24) away from the bearing (15). A spring (52);
Further comprising
The compressor is characterized in that an inlet (63) of the bleed passage is provided closer to the bearing (15) than the return spring (52). The compressor according to claim 1 or 2,
The compressor is characterized in that the passage expanding portion (67) is provided above the main body portion (66) and is inclined downward from the crank chamber (5) side toward the bearing (15) side. .

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