JP2017150438A - Piston type swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability of a sliding bearing while actualizing good lubrication between the sliding bearing and a rotor.SOLUTION: A rotor 17A has an internal passage 30. In the rotation phase of a top dead center corresponding part 19a of a swash plate 19 to a piston 22, an opening 43a of the internal passage 30 at the side of a second supporting part 42 is at a phase position on the opposite side to the top dead center corresponding part 19a. As a result, when radial load works on the second supporting part 42 in association with the movement of the rotor 17A to the side of the top dead center corresponding part 19a of the swash plate 19 in the radial direction of a rotary shaft 17, the opening edge of the opening 43a of the internal passage 30 hardly slide on the second supporting part 42. Then, the lubricating oil is supplied from the inside of a swash plate chamber 16 directly between the second supporting part 42 and the rotary shaft 17 and in addition the lubricating oil is supplied via the internal passage 30 between the second supporting part 42 and the rotary shaft 17, thus increasing the amount of the lubricating oil to be supplied between the second supporting part 42 and the rotary shaft 17.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a piston-type swash plate compressor.

  The piston-type swash plate compressor includes a housing having a swash plate chamber and a cylinder block in which a plurality of cylinder bores are formed. A rotating body including a rotating shaft is accommodated in the housing. Both end portions of the rotating body are rotatably supported by the housing via sliding bearings as radial bearings. The swash plate chamber houses a swash plate that rotates by obtaining a driving force from a rotating shaft. A piston is accommodated in each cylinder bore so as to be able to reciprocate. Each piston is anchored to the outer periphery of the swash plate via a pair of shoes. The rotational movement of the swash plate accompanying the rotation of the rotary shaft is converted into the reciprocating linear movement of the piston through the shoe. Then, the movement of the piston from the top dead center to the bottom dead center causes the refrigerant to be sucked into the cylinder bore from the suction chamber, and the movement from the bottom dead center to the top dead center causes the refrigerant in the cylinder bore to reach a predetermined pressure. Until it is compressed to the discharge chamber.

  The refrigerant contains lubricating oil, and the lubricating oil contributes to lubrication of the sliding parts accommodated in the housing. In a piston-type swash plate compressor, in a configuration in which a rotating body is rotatably supported using a sliding bearing, the sliding bearing and the rotating body are used in order to improve lubrication between the sliding bearing and the rotating body. It is necessary to form an oil film between the two. However, if the amount of lubricating oil supplied between the sliding bearing and the rotating body is small, it is difficult to form an oil film between the sliding bearing and the rotating body, and good lubrication between the sliding bearing and the rotating body is achieved. It becomes impossible to keep things.

  Therefore, for example, Patent Document 1 discloses that an internal passage communicating with the inside of the housing is formed in the rotating body, and lubricating oil in the housing is supplied between the radial bearing and the rotating body via the internal passage. . According to this, in addition to the lubricating oil being directly supplied from the housing to the radial bearing and the rotating body, the lubricating oil is supplied between the radial bearing and the rotating body via the internal passage. Therefore, the amount of lubricating oil supplied between the radial bearing and the rotating body is increased, and the lubrication between the radial bearing and the rotating body is improved.

JP 2008-121536 A

  By the way, in the piston type swash plate compressor, when the compression reaction force from the piston acts on the swash plate, the rotating body swings. In particular, the compression reaction force from the piston is likely to act on the top dead center corresponding portion of the swash plate that corresponds to the top dead center of the piston, and the rotating body has a compression reaction force acting on the swash plate. Therefore, it is easy to move to the top dead center corresponding side of the swash plate in the radial direction of the rotation shaft. Therefore, a radial load accompanying the movement of the swash plate toward the top dead center side acts on the sliding bearing in the radial direction of the rotating shaft of the rotating body. At this time, consider a case where the sliding bearing side opening in the internal passage is in the same phase position as the top dead center corresponding portion in the rotational phase of the top dead center corresponding portion of the swash plate. In this case, when a radial load associated with the movement of the swash plate toward the top dead center side in the radial direction of the rotating shaft in the rotating body acts on the sliding bearing, the opening edge of the opening on the sliding bearing side in the internal passage Since the slide slides in a state of being pressed against the slide bearing, the slide bearing is likely to be worn, and the durability of the slide bearing is reduced.

  The present invention has been made to solve the above-mentioned problems, and its object is to improve the durability of the sliding bearing while improving the lubrication between the sliding bearing and the rotating body. An object of the present invention is to provide a piston-type swash plate compressor.

  A piston-type swash plate compressor that solves the above problems includes a swash plate chamber, a housing including a cylinder block having a plurality of cylinder bores, a rotating body that includes a rotating shaft that is housed in the housing, and is housed in the swash plate chamber. A swash plate that rotates by obtaining a driving force from the rotating shaft, a piston that is moored to the swash plate and is reciprocally received in the cylinder bore, and a reciprocating linear motion of the piston. A piston-type swash plate compressor in which the rotating body is rotatably supported by the housing via a sliding bearing, and the rotating body communicates with the housing. And having an internal passage for supplying lubricating oil contained in the refrigerant in the housing between the sliding bearing and the rotating body, the internal passage on the sliding bearing side Mouth is said to the top dead center corresponding portion in the rotation phase of the dead point corresponding part on a corresponding portion of the top dead center of the piston in the swash plate is in the phase position of the opposite side.

  According to this, the compression reaction force from the piston acts on the swash plate, and the radial load accompanying the movement of the swash plate toward the top dead center side in the radial direction of the rotating shaft of the rotating body acts on the sliding bearing. Sometimes, the opening edge of the opening on the sliding bearing side in the internal passage is difficult to slide on the sliding bearing. In addition to the fact that the lubricating oil is directly supplied from the inside of the housing to the sliding bearing and the rotating body, the lubricating oil is supplied between the sliding bearing and the rotating body via the internal passage. The amount of lubricating oil supplied between the sliding bearing and the rotating body increases. As a result, it is possible to improve the durability of the sliding bearing while improving the lubrication between the sliding bearing and the rotating body.

  In the piston-type swash plate compressor, the opening on the sliding bearing side in the internal passage is directly between the sliding bearing and the rotating body and directly between the sliding bearing and the rotating body. It is preferable to open to the upstream side in the flow direction of the supplied lubricating oil.

  According to this, the lubricating oil supplied between the sliding bearing and the rotating body via the internal passage is upstream in the flow direction of the lubricating oil supplied directly from the housing to the sliding bearing and the rotating body. Supplied from Therefore, the lubricating oil can be efficiently supplied between the sliding bearing and the rotating body via the internal passage, and the lubrication between the sliding bearing and the rotating body can be further improved.

  In the piston-type swash plate compressor, a suction chamber and a discharge chamber formed in the housing, an air supply passage for supplying refrigerant from the discharge chamber to the swash plate chamber, and a refrigerant in the swash plate chamber are discharged to the suction chamber. And the internal passage forms a part of the extraction passage and extends along the axial direction of the rotating shaft, and is continuous with the internal passage and is connected to the sliding bearing. It is preferable that the in-shaft passage includes a large-diameter passage portion that communicates with the lubrication hole and a small-diameter passage portion that is smaller in diameter than the large-diameter passage portion.

  According to this, since the centrifugal force acting on the lubricating oil in the large diameter passage portion is larger than the centrifugal force acting on the lubricating oil in the small diameter passage portion, the lubricating oil in the shaft passage accumulates in the large diameter passage portion. It becomes easy. As a result, since the lubricating oil is easily guided to the lubricating hole, the lubricating oil is easily supplied between the sliding bearing and the rotating body.

  In the piston-type swash plate compressor, a capacity control valve for adjusting a pressure in the swash plate chamber by adjusting an opening degree of the air supply passage is disposed on the air supply passage. A first throttle is formed in the passage, and the first throttle is disposed downstream of the in-shaft passage in the refrigerant flow direction in the extraction passage, and the large diameter in the in-shaft passage. It is preferable that a second throttle is provided downstream of the passage portion in the flow direction of the refrigerant, and the flow passage cross-sectional area of the second throttle is larger than the flow passage cross-sectional area of the first throttle. .

  According to this, since the flow path cross-sectional area of the second throttle is larger than the flow path cross-sectional area of the first throttle, the second throttle is provided downstream of the large-diameter passage portion in the in-axis passage in the refrigerant flow direction. However, the function of the first aperture is not affected. Then, as compared with the case where the second throttle is not disposed downstream of the large-diameter passage portion in the in-axis passage in the refrigerant flow direction, the lubricating oil contained in the refrigerant passing through the in-axis passage is larger than the large-diameter passage. Since it becomes easy to be led to the lubricating hole through the portion, the lubricating oil is easily supplied between the sliding bearing and the rotating body.

In the piston-type swash plate compressor, it is preferable that the second diaphragm is rotatable integrally with the rotating body and is located at the rotation center of the rotating shaft.
The lubricating oil in the in-shaft passage easily moves to the outer peripheral side of the in-shaft passage by the centrifugal force of the rotating body. At this time, since the second diaphragm is located at the rotation center of the rotation shaft, the lubricating oil is guided to the lubrication hole as compared with the case where the second diaphragm is arranged at a position shifted from the rotation center of the rotation shaft. It becomes easy.

In the piston-type swash plate compressor, the second throttle is preferably provided on an attachment member attached to the in-shaft passage.
According to this, a 2nd aperture_diaphragm | restriction can be provided in an in-axis passage only by attaching an attachment member to an in-axis passage. Therefore, since it is not necessary to process the rotating shaft in order to provide the second diaphragm in the in-shaft passage, the structure of the rotating shaft can be simplified.

  According to the present invention, it is possible to improve the durability of the sliding bearing while improving the lubrication between the sliding bearing and the rotating body.

A side sectional view showing a variable capacity type swash plate type compressor in an embodiment. A partial enlarged side sectional view of a variable capacity swash plate compressor.

  Hereinafter, an embodiment in which a piston-type swash plate compressor is embodied as a variable displacement swash plate compressor will be described with reference to FIGS. 1 and 2. The variable capacity swash plate compressor of the present embodiment is mounted on a vehicle and used for a vehicle air conditioner.

  As shown in FIG. 1, the housing 11 of the variable displacement swash plate compressor 10 includes a cylinder block 12, a front housing 13 connected to one end (front end) of the cylinder block 12, and the other end (rear side) of the cylinder block 12. And a rear housing 15 connected to the end via a valve / port forming body 14. In the housing 11, a swash plate chamber 16 is defined in a space surrounded by the cylinder block 12 and the front housing 13. A rotating shaft 17 is accommodated in the housing 11. In the swash plate chamber 16, a lug plate 18 is rotatably provided on the rotary shaft 17. The rotating shaft 17 and the lug plate 18 constitute a rotating body 17 </ b> A including the rotating shaft 17 accommodated in the housing 11.

  The front housing 13 is formed with a through hole 13a through which the rotary shaft 17 passes. One end of the rotating shaft 17 protrudes from the front housing 13 through the through hole 13a, and is connected to the vehicle engine E as an external drive source through the power transmission mechanism PT. In the present embodiment, the power transmission mechanism PT is a constant transmission type clutchless mechanism (for example, a combination of a belt and a pulley).

  The swash plate chamber 16 accommodates a swash plate 19 that rotates by obtaining a driving force from the rotary shaft 17 and that can tilt with respect to a direction orthogonal to the rotation axis L of the rotary shaft 17. The swash plate 19 is supported by the rotary shaft 17 so as to be slidable in the swash plate chamber 16. Between the lug plate 18 and the swash plate 19, the swash plate 19 is urged in a direction to reduce the inclination angle of the swash plate 19 (inclination angle of the swash plate 19) with respect to the direction orthogonal to the rotation axis L of the rotation shaft 17. A biasing spring 20 is disposed. Further, a hinge mechanism 21 is interposed between the lug plate 18 and the swash plate 19. The swash plate 19 is synchronized with the lug plate 18 and the rotary shaft 17 by the biasing force of the biasing spring 20, the hinge connection with the lug plate 18 via the hinge mechanism 21, and the support of the rotary shaft 17. And can be tilted with respect to the rotation shaft 17 while being slid in the axial direction of the rotation shaft 17.

  In the cylinder block 12, a plurality of cylinder bores 12a formed so as to penetrate in the axial direction of the cylinder block 12 are arranged around the rotation shaft 17 (only one cylinder bore 12a is shown in FIG. 1). A piston 22 is accommodated in each cylinder bore 12a so as to be able to reciprocate. Both openings of each cylinder bore 12 a are closed by a valve / port forming body 14 and a piston 22. In each cylinder bore 12a, a compression chamber 23 whose volume changes according to the reciprocating motion of the piston 22 is defined. Each piston 22 is anchored to the outer periphery of the swash plate 19 via a pair of shoes 24. Then, the rotational movement of the swash plate 19 accompanying the rotation of the rotary shaft 17 is converted into the reciprocating linear movement of the piston 22 via the shoe 24. Therefore, the shoe 24 is a conversion mechanism that converts the rotational movement of the swash plate 19 into the reciprocating linear movement of the piston 22.

  A discharge chamber 25 is defined between the rear housing 15 and the valve / port forming body 14, and a suction chamber 26 is annularly defined outside the discharge chamber 25. Further, the valve / port forming body 14 is formed with a discharge port 25h communicating with the discharge chamber 25 and a discharge valve 25v opening and closing the discharge port 25h, and with a suction port 26h communicating with the suction chamber 26, and a suction port A suction valve 26v that opens and closes 26h is formed. A retainer plate 14 a that regulates the opening degree of the discharge valve 25 v is attached to the valve / port formation body 14. The retainer plate 14a is fastened to the valve / port forming body 14 by bolts 14b.

  The refrigerant (carbon dioxide in this embodiment) in the suction chamber 26 is sucked into the cylinder bore 12a through the suction port 26h and the suction valve 26v by the movement from the top dead center to the bottom dead center of the piston 22. The refrigerant sucked into the cylinder bore 12a is compressed to a predetermined pressure by the movement from the bottom dead center to the top dead center of the piston 22, and is discharged from the discharge port 25h to the discharge chamber 25 by pushing out the discharge valve 25v. . Therefore, the suction chamber 26 is a suction pressure region, and the discharge chamber 25 is a discharge pressure region.

  The discharge chamber 25 and the swash plate chamber 16 are connected to each other by an air supply passage 27 that passes through the rear housing 15, the valve / port forming body 14, and the cylinder block 12. The air supply passage 27 supplies the refrigerant in the discharge chamber 25 to the swash plate chamber 16. An electromagnetic capacity control valve 27v is attached to the rear housing 15. The capacity control valve 27v is disposed on the air supply passage 27. The capacity control valve 27v of the present embodiment senses the pressure of the refrigerant (suction pressure) supplied from the suction chamber 26 to the capacity control valve 27v, so that the valve body moves and the valve opening is adjusted. The capacity control valve 27v adjusts the pressure in the swash plate chamber 16 by adjusting the opening of the air supply passage 27.

  Between the front housing 13 and the rotating shaft 17 in the through hole 13a, a shaft seal device 13s is provided for preventing the refrigerant from leaking out of the housing 11 through the through hole 13a. In the present embodiment, the shaft seal device 13s is a mechanical seal. The front housing 13 is provided with a supply passage 13d that communicates the upper portion of the swash plate chamber 16 in the direction of gravity with the accommodation space 13k in which the shaft seal device 13s is accommodated in the through hole 13a. Then, the lubricating oil contained in the refrigerant accumulated at the bottom of the swash plate chamber 16 below the gravity direction is wound up together with the refrigerant by the rotation of the swash plate 19 and the lug plate 18 and adheres to the entire inner wall surface of the front housing 13. And flows into the supply passage 13d by gravity. The lubricating oil that has flowed into the supply passage 13d is supplied to the accommodation space 13k in the through hole 13a via the supply passage 13d, and is supplied to the mechanical seal that is the shaft seal device 13s.

  On the end face of the cylinder block 12 on the valve / port forming body 14 side, a recess 12h is formed in which the other end of the rotating shaft 17 is disposed inside. A cylindrical positioning member 29 that positions the rotary shaft 17 in the axial direction is disposed inside the recess 12h. The positioning member 29 is press-fitted into the outer peripheral portion of the other end portion of the rotating shaft 17. Further, the valve / port forming body 14 is formed with a communication portion 14 c that communicates the inside of the recess 12 h and the suction chamber 26. The communication part 14 c has a first diaphragm 31.

  The lug plate 18 has a cylindrical bearing portion 18a inserted from the swash plate chamber 16 into the through hole 13a. One end of the rotating shaft 17 is inserted into the bearing portion 18a. The bearing portion 18 a is rotatably supported by an annular first support portion 41 provided in the front housing 13. A portion of the outer peripheral surface of the bearing portion 18a that is rotatably supported by the first support portion 41 is coated. The coating is, for example, a fluororesin. A space between the inner peripheral surface of the first support portion 41 and the outer peripheral surface of the bearing portion 18a communicates with the accommodation space 13k. Lubricating oil is directly supplied from the swash plate chamber 16 between the inner peripheral surface of the first support portion 41 and the outer peripheral surface of the bearing portion 18a, and an oil film is formed between the first support portion 41 and the bearing portion 18a. ing. The first support portion 41 functions as a sliding bearing that rotatably supports one end portion in the axial direction of the rotating shaft 17 in the rotating body 17A.

  The other end portion of the rotating shaft 17 is rotatably supported by an annular second support portion 42 provided in the cylinder block 12. A portion of the outer peripheral surface of the rotating shaft 17 that is rotatably supported by the second support portion 42 is coated. The coating is, for example, a fluororesin. The inner peripheral surface of the second support portion 42 and the outer peripheral surface of the rotary shaft 17 communicate with the recess 12h. Lubricating oil is directly supplied from the swash plate chamber 16 between the inner peripheral surface of the second support portion 42 and the outer peripheral surface of the rotary shaft 17, and an oil film is formed between the second support portion 42 and the rotary shaft 17. ing. The second support portion 42 functions as a slide bearing that rotatably supports the other end portion of the rotating body 17A in the axial direction of the rotating shaft 17.

  The inner diameter of the first support part 41 is larger than the inner diameter of the second support part 42. Therefore, the gap between the inner peripheral surface of the first support portion 41 and the outer peripheral surface of the bearing portion 18 a is less than that between the inner peripheral surface of the second support portion 42 and the outer peripheral surface of the rotary shaft 17. It ’s hard to be.

  The rotating shaft 17 has an internal passage 30. The internal passage 30 includes an in-axis passage 17 a that extends along the axial direction of the rotary shaft 17 and a communication passage 17 b that extends along the radial direction of the rotary shaft 17. One end of the in-shaft passage 17 a communicates with the communication passage 17 b, and the other end opens to the end face of the other end of the rotating shaft 17 and communicates with the inside of the positioning member 29. The communication path 17b communicates with the accommodation space 13k in the through hole 13a.

  The internal passage 30 includes a through hole 17h. The through hole 17h extends along the radial direction of the rotary shaft 17 and communicates the swash plate chamber 16 and the middle of the in-shaft passage 17a. Further, the internal passage 30 includes a lubrication hole 43 that is continuous with the in-axis passage 17a and extends toward the second support portion. The lubrication hole 43 is located downstream of the through-hole 17h in the coolant flow direction with respect to the in-axis passage 17a. An opening 43a on the second support portion 42 side in the lubrication hole 43 (an opening on the second support portion 42 side in the internal passage 30) is a top dead center corresponding to the top dead center of the piston 22 in the swash plate 19. The rotational phase of the corresponding portion 19a is at the phase position opposite to the top dead center corresponding portion 19a.

  As shown in FIG. 2, the opening 43 a of the lubricating hole 43 is directly supplied from the swash plate chamber 16 between the second support portion 42 and the rotary shaft 17 between the second support portion 42 and the rotary shaft 17. It opens to the upstream side in the flow direction of the lubricating oil. At this time, the opening 43a of the lubrication hole 43 and the swash plate chamber 16 are disposed at a position where they communicate with each other via the second support portion 42 and the rotary shaft 17, and the opening 43a of the lubrication hole 43 is inclined. It does not communicate directly with the board chamber 16.

  The in-shaft passage 17a includes a large-diameter passage portion 171a communicating with the lubrication hole 43 and a small-diameter passage portion 172a having a smaller diameter than the large-diameter passage portion 171a. In the shaft passage 17a, a portion around the lubricating hole 43 communicating with the lubricating hole 43 is a large diameter passage portion 171a, and the other portion is a small diameter passage portion 172a.

  A cylindrical attachment member 34 having a second diaphragm 32 is attached to the other end side of the rotary shaft 17 in the in-shaft passage 17a. The attachment member 34 is press-fitted into the in-shaft passage 17a. Therefore, the second diaphragm 32 is provided on the attachment member 34 attached to the in-shaft passage 17a, and can rotate integrally with the rotary shaft 17. The second throttle 32 is provided downstream of the large-diameter passage portion 171a in the refrigerant flow direction. The channel cross-sectional area of the second throttle 32 is larger than the channel cross-sectional area of the first throttle 31. The second diaphragm 32 is located at the rotation center of the rotation shaft 17.

  The refrigerant in the swash plate chamber 16 is discharged (refluxed) to the suction chamber 26 through the through hole 17h, the shaft passage 17a, the second throttle 32, the inside of the positioning member 29, the recess 12h, and the communication portion 14c. Therefore, the through hole 17h, the in-shaft passage 17a, the second throttle 32, the inside of the positioning member 29, the recess 12h, and the communication portion 14c constitute an extraction passage 28 for discharging the refrigerant in the swash plate chamber 16 to the suction chamber 26. . Therefore, the bleed passage 28 has a first throttle 31. The first throttle 31 is disposed in the bleed passage 28 on the downstream side of the in-shaft passage 17a in the refrigerant flow direction. The in-axis passage 17a constitutes a part of the extraction passage 28. The supply passage 13d, the accommodation space 13k, and the communication passage 17b also constitute part of the extraction passage 28.

  The refrigerant discharged from the swash plate chamber 16 to the suction chamber 26 via the extraction passage 28 is decompressed when passing through the first throttle 31. Therefore, the swash plate chamber 16 is at a higher pressure than the suction chamber 26. Therefore, the swash plate chamber 16 obtains an intermediate pressure that is lower than the pressure of the discharge chamber 25 and higher than the pressure of the suction chamber 26.

  In the variable displacement swash plate compressor 10, when the air conditioner switch is turned off and the energization to the displacement control valve 27 v is stopped, the displacement control valve 27 v is in an open state in which the air supply passage 27 is opened. . Then, the refrigerant is supplied from the discharge chamber 25 to the swash plate chamber 16 through the air supply passage 27, and the pressure in the swash plate chamber 16 approaches the pressure in the discharge chamber 25. Thereby, the inclination angle of the swash plate 19 is reduced, the stroke of the piston 22 is reduced, and the discharge capacity is reduced.

  On the other hand, when the air conditioner switch is turned on and the capacity control valve 27v is energized, the capacity control valve 27v is in a closed state in which the air supply passage 27 is closed. As a result, the supply of the refrigerant from the discharge chamber 25 to the swash plate chamber 16 through the air supply passage 27 is not performed, and the refrigerant in the swash plate chamber 16 is discharged to the suction chamber 26 through the extraction passage 28, and the swash plate chamber The pressure of 16 approaches the pressure of the suction chamber 26. As a result, the inclination angle of the swash plate 19 increases, the stroke of the piston 22 increases, and the discharge capacity increases.

  Thus, the swash plate chamber 16 functions as a control pressure chamber that changes the tilt angle of the swash plate 19. In the variable capacity swash plate compressor 10 of the present embodiment, the capacity control valve 27v is disposed in the air supply passage 27, and the valve opening degree of the capacity control valve 27v is adjusted to supply the air supply path from the discharge chamber 25. By controlling the supply amount of the refrigerant supplied to the swash plate chamber 16 through 27, so-called “insertion control” is performed to control the pressure in the swash plate chamber 16.

Next, the operation of this embodiment will be described.
The lubricating oil directly supplied from the swash plate chamber 16 between the inner peripheral surface of the first support portion 41 and the outer peripheral surface of the bearing portion 18a contributes to lubrication between the first support portion 41 and the bearing portion 18a. Further, the lubricating oil directly supplied from the swash plate chamber 16 between the inner peripheral surface of the second support portion 42 and the outer peripheral surface of the rotary shaft 17 contributes to lubrication between the second support portion 42 and the rotary shaft 17. To do. Since the inner diameter of the first support portion 41 is larger than the inner diameter of the second support portion 42, the inner periphery of the second support portion 42 is between the inner peripheral surface of the first support portion 41 and the outer peripheral surface of the bearing portion 18 a. Compared with the space between the surface and the outer peripheral surface of the rotary shaft 17, it is difficult for the lubricating oil to be insufficient.

  Lubricating oil supplied from the swash plate chamber 16 to the accommodation space 13k via the supply passage 13d, or the accommodation space passing between the inner peripheral surface of the first support portion 41 and the outer peripheral surface of the bearing portion 18a from the swash plate chamber 16. The lubricating oil that has flowed into 13k flows into the in-shaft passage 17a via the communication passage 17b. Further, the lubricating oil contained in the refrigerant from the swash plate chamber 16 toward the through hole 17h flows into the in-shaft passage 17a through the through hole 17h. Such lubricating oil flowing into the shaft passage 17a passes through the shaft passage 17a while adhering to the inner peripheral surface of the shaft passage 17a by the centrifugal force of the rotating shaft 17.

  At this time, the centrifugal force acting on the lubricating oil in the large-diameter passage portion 171a is larger than the centrifugal force acting on the lubricating oil in the small-diameter passage portion 172a. It becomes easy to accumulate in the part 171a. Moreover, since the cylindrical attachment member 34 which has the 2nd aperture_diaphragm | restriction 32 is attached to the other end side of the rotating shaft 17 in the axial passage 17a, the flow of a refrigerant | coolant rather than the large diameter passage part 171a in the axial passage 17a. Compared with the case where the second restrictor 32 is not disposed on the downstream side in the direction, the lubricating oil passing through the in-shaft passage 17a is easily guided to the lubricating hole 43 through the large-diameter passage portion 171a. At this time, since the flow passage cross-sectional area of the second restrictor 32 is larger than the flow passage cross-sectional area of the first restrictor 31, even if the second restrictor 32 is provided in the in-axis passage 17a, the function of the first restrictor 31 is affected. There is no effect. The lubricating oil in the in-shaft passage 17a easily moves to the outer peripheral side of the in-shaft passage 17a by the centrifugal force of the rotating shaft 17. At this time, since the second diaphragm 32 is located at the rotation center of the rotating shaft 17, the lubricating oil is lubricated as compared with the case where the second diaphragm 32 is disposed at a position shifted from the rotation center of the rotating shaft 17. It becomes easy to be guided to the hole 43. Then, the oil is supplied between the second support portion 42 and the rotary shaft 17 through the lubrication hole 43. Therefore, the internal passage 30 communicates with the swash plate chamber 16 (housing 11) and supplies lubricating oil contained in the refrigerant in the swash plate chamber 16 between the second support portion 42 and the rotating shaft 17.

  The opening 43 a of the lubrication hole 43 flows between the second support 42 and the rotary shaft 17, and the flow of lubricating oil directly supplied from the swash plate chamber 16 to between the second support 42 and the rotary shaft 17. Open upstream in the direction. For this reason, the lubricating oil supplied between the second support portion 42 and the rotary shaft 17 from the in-shaft passage 17 a via the lubrication hole 43 passes between the second support portion 42 and the rotary shaft 17 from the swash plate chamber 16. Supplied from the upstream side in the flow direction of the lubricating oil supplied directly to In this way, in addition to the lubricating oil being directly supplied from the swash plate chamber 16 between the second support portion 42 and the rotary shaft 17, the second support portion 42 and the rotary shaft 17 are connected via the internal passage 30. Therefore, the amount of lubricating oil supplied between the second support portion 42 and the rotary shaft 17 increases. As a result, the lubrication between the second support portion 42 and the rotating shaft 17 is good. The lubricating oil that has passed between the second support portion 42 and the rotary shaft 17 is discharged to the suction chamber 26 through the recess 12h and the communication portion 14c.

  In the variable displacement swash plate compressor 10, when the compression reaction force from the piston 22 acts on the swash plate 19, the rotating body 17 </ b> A swings. Particularly, in the swash plate 19, the compression reaction force from the piston 22 is likely to act on the top dead center corresponding portion 19a of the piston 22 in the swash plate 19, and the rotating body 17A is caused by the compression reaction force acting on the swash plate 19. It is easy to move to the top dead center corresponding part 19 a side of the swash plate 19 in the radial direction of the rotating shaft 17. Therefore, a radial load accompanying the movement of the swash plate 19 toward the top dead center 19a side acts on the first support portion 41 and the second support portion 42 in the radial direction of the rotating shaft 17 in the rotating body 17A.

  Therefore, the opening 43a of the lubricating hole 43 is in a phase position opposite to the top dead center corresponding portion 19a in the rotational phase of the top dead center corresponding portion 19a of the piston 22 in the swash plate 19. According to this, the compressive reaction force from the piston 22 acts on the swash plate 19, and the radial load accompanying the movement of the swash plate 19 toward the top dead center corresponding portion 19a in the radial direction of the rotating shaft 17 in the rotating body 17A. When it acts on the 2nd support part 42, the opening edge part of the opening part 43a of the lubrication hole 43 becomes difficult to slide to the 2nd support part 42. Therefore, the durability of the second support portion 42 is improved.

In the above embodiment, the following effects can be obtained.
(1) The rotating body 17A has an internal passage 30 that communicates with the swash plate chamber 16 and supplies lubricating oil contained in the refrigerant in the swash plate chamber 16 between the second support portion 42 and the rotating shaft 17. The opening 43a on the second support portion 42 side in the internal passage 30 is in a phase position opposite to the top dead center corresponding portion 19a in the rotational phase of the top dead center corresponding portion 19a of the piston 22 in the swash plate 19. According to this, the compressive reaction force from the piston 22 acts on the swash plate 19, and the radial load accompanying the movement of the swash plate 19 toward the top dead center corresponding portion 19a in the radial direction of the rotating shaft 17 in the rotating body 17A. When it acts on the 2nd support part 42, the opening edge part of the opening part 43a of the internal channel | path 30 becomes difficult to slide to the 2nd support part 42. FIG. The lubricating oil is directly supplied from the inside of the swash plate chamber 16 to the space between the second support portion 42 and the rotary shaft 17, and in addition, between the second support portion 42 and the rotary shaft 17 via the internal passage 30. Therefore, the amount of lubricating oil supplied between the second support portion 42 and the rotating shaft 17 increases. As a result, it is possible to improve the durability of the second support portion 42 while improving the lubrication between the second support portion 42 and the rotating shaft 17.

  (2) The opening 43 a of the internal passage 30 is lubricated between the second support portion 42 and the rotary shaft 17 and directly supplied from the swash plate chamber 16 to the space between the second support portion 42 and the rotary shaft 17. It opens on the upstream side in the flow direction. According to this, the lubricating oil supplied between the second support portion 42 and the rotary shaft 17 via the internal passage 30 is directly from the inside of the swash plate chamber 16 to between the second support portion 42 and the rotary shaft 17. It is supplied from the upstream side in the flow direction of the supplied lubricating oil. Therefore, the lubricating oil can be efficiently supplied between the second support portion 42 and the rotary shaft 17 via the internal passage 30, and the lubrication between the second support portion 42 and the rotary shaft 17 can be further improved. Can be.

  (3) The in-axis passage 17a has a large-diameter passage portion 171a communicating with the lubrication hole 43 and a small-diameter passage portion 172a having a smaller diameter than the large-diameter passage portion 171a. According to this, since the centrifugal force acting on the lubricating oil in the large-diameter passage portion 171a is larger than the centrifugal force acting on the lubricating oil in the small-diameter passage portion 172a, the lubricating oil in the shaft passage 17a is large. It becomes easy to collect in the diameter passage portion 171a. As a result, since the lubricating oil is easily guided to the lubricating hole 43, the lubricating oil is easily supplied between the second support portion 42 and the rotary shaft 17.

  (4) The channel cross-sectional area of the second throttle 32 is larger than the channel cross-sectional area of the first throttle 31. According to this, even if the second diaphragm 32 is provided in the in-shaft passage 17a, the function of the first diaphragm 31 is not affected. Compared with the case where the second throttle 32 is not disposed on the downstream side in the refrigerant flow direction with respect to the large-diameter passage portion 171a in the in-shaft passage 17a, the lubricating oil passing through the in-shaft passage 17a is lubricated by the lubricating hole 43. Therefore, the lubricating oil is easily supplied between the second support portion 42 and the rotary shaft 17.

  (5) The second diaphragm 32 is located at the rotation center of the rotation shaft 17. The lubricating oil in the in-shaft passage 17a easily moves to the outer peripheral side of the in-shaft passage 17a by the centrifugal force of the rotating shaft 17. At this time, since the second diaphragm 32 is located at the rotation center of the rotating shaft 17, the lubricating oil is lubricated as compared with the case where the second diaphragm 32 is disposed at a position shifted from the rotation center of the rotating shaft 17. It becomes easy to be guided to the hole 43.

  (6) The 2nd aperture_diaphragm | restriction 32 is provided in the attachment member 34 attached to the in-shaft channel | path 17a. According to this, the 2nd aperture_diaphragm | restriction 32 can be provided in the axial passage 17a only by attaching the attachment member 34 to the axial passage 17a. Therefore, since it is not necessary to process the rotating shaft 17 in order to provide the 2nd aperture_diaphragm | restriction 32 in the axial channel | path 17a, the structure of the rotating shaft 17 can be simplified.

  (7) Coating is applied to a portion of the outer peripheral surface of the bearing portion 18a that is rotatably supported by the first support portion 41 and a portion of the outer peripheral surface of the rotary shaft 17 that is rotatably supported by the second support portion 42. Has been. According to this, the slidability between the bearing portion 18a and the first support portion 41 and between the rotary shaft 17 and the second support portion 42 can be improved.

In addition, you may change the said embodiment as follows.
In the embodiment, for example, the tip of the bolt 14b used to fasten the retainer plate 14a to the valve / port forming body 14 is extended to the vicinity of the end of the rotating shaft 17 or to the position where it enters the shaft passage 17a. Alternatively, the second diaphragm 32 may be formed by the rotation shaft 17 and the bolt 14b.

In the embodiment, the inner surface of the rotating shaft 17 may be processed to provide the second diaphragm 32 in the in-axis passage 17a.
In the embodiment, the second diaphragm 32 may be disposed at a position shifted from the rotation center of the rotation shaft 17.

In the embodiment, the second diaphragm 32 may not be provided.
In the embodiment, the inner diameter of the in-axis passage 17a may be constant.
In the embodiment, the opening position of the opening 43a of the internal passage 30 is not particularly limited as long as it opens between the second support portion 42 and the rotating shaft 17.

In the embodiment, a configuration in which a bush is provided as a sliding bearing between the bearing portion 18a and the first support portion 41 or between the rotating shaft 17 and the second support portion 42 may be employed.
In the embodiment, the lug plate 18 may not have the cylindrical bearing portion 18a inserted from the swash plate chamber 16 into the through hole 13a. Then, one end portion of the rotation shaft 17 may be rotatably supported by the first support portion 41.

In the embodiment, the portion of the outer peripheral surface of the bearing portion 18a that is directly supported rotatably by the first support portion 41 may not be coated.
In the embodiment, the portion of the outer peripheral surface of the rotating shaft 17 that is rotatably supported by the second support portion 42 may not be coated.

  In the embodiment, the first support portion 41 may be coated without coating the portion of the outer peripheral surface of the bearing portion 18a that is directly supported rotatably by the first support portion 41.

In the embodiment, the portion of the outer peripheral surface of the bearing portion 18a that is rotatably supported by the first support portion 41 and the first support portion 41 may be coated.
In the embodiment, the second support portion 42 may be coated without coating the portion of the outer peripheral surface of the rotating shaft 17 that is rotatably supported by the second support portion 42.

In the embodiment, the portion of the outer peripheral surface of the rotating shaft 17 that is directly supported rotatably by the second support portion 42 and the second support portion 42 may be coated.
In the embodiment, a capacity control valve is provided in the bleed passage 28 and the variable capacity swash plate compressor 10 is sucked from the swash plate chamber 16 through the bleed passage 28 by adjusting the valve opening of the capacity control valve. It may be configured to perform so-called “extraction-side control” in which the pressure of the swash plate chamber 16 is controlled by controlling the discharge amount of the refrigerant discharged into the chamber 26.

In the embodiment, a control pressure chamber may be formed separately from the swash plate chamber 16, and the tilt angle of the swash plate 19 may be changed by controlling the pressure in the control pressure chamber.
In the embodiment, the power transmission mechanism PT may be a clutch mechanism that can select transmission and interruption of power by electric control from the outside.

In the embodiment, the piston-type swash plate compressor may be a fixed capacity type.
In the embodiment, the variable capacity swash plate compressor 10 may not be used for a vehicle air conditioner, and may be used for other air conditioners.

  In the embodiment, carbon dioxide is used as the refrigerant. However, for example, chlorofluorocarbon may be used as the refrigerant.

  DESCRIPTION OF SYMBOLS 10 ... Variable displacement type swash plate type compressor which is a piston type swash plate compressor, 11 ... Housing, 12 ... Cylinder block, 12a ... Cylinder bore, 16 ... Swash plate chamber, 17 ... Rotating shaft, 17a ... In-shaft passage, 17A ... Rotation Body 19 swash plate 19a top dead center corresponding part 22 piston piston 24 conversion shoe 25 discharge chamber 26 suction chamber 27 air supply passage 27v capacity control valve 28 Bleed passage, 30 internal passage, 31 first throttle, 32 second throttle, 34 mounting member, 41 first support functioning as a sliding bearing, 42 second support functioning as a sliding bearing, 43 ... Lubrication hole, 43a ... Opening part, 171a ... Large diameter passage part, 172a ... Small diameter passage part.

Claims (6)

A housing including a swash plate chamber and a cylinder block having a plurality of cylinder bores;
A rotating body including a rotating shaft housed in the housing;
A swash plate housed in the swash plate chamber and rotated by obtaining a driving force from the rotating shaft;
A piston moored to the swash plate and housed in the cylinder bore so as to reciprocate;
A conversion mechanism for converting the rotational movement of the swash plate into the reciprocating linear movement of the piston,
A piston-type swash plate compressor in which the rotating body is rotatably supported by the housing via a sliding bearing;
The rotating body has an internal passage that communicates with the housing and supplies lubricating oil contained in the refrigerant in the housing between the sliding bearing and the rotating body,
The opening on the sliding bearing side in the internal passage is a phase on the opposite side of the top dead center corresponding portion in the rotational phase of the top dead center corresponding portion which is the corresponding portion with the top dead center of the piston in the swash plate. Piston-type swash plate compressor characterized by being in position.   The opening on the sliding bearing side in the internal passage is between the sliding bearing and the rotating body in the flow direction of the lubricating oil directly supplied from the housing to the sliding bearing and the rotating body. 2. The piston-type swash plate compressor according to claim 1, wherein the piston-type swash plate compressor is opened upstream. A suction chamber and a discharge chamber formed in the housing;
An air supply passage for supplying the refrigerant in the discharge chamber to the swash plate chamber;
A bleed passage for discharging the refrigerant in the swash plate chamber to the suction chamber,
The internal passage forms a part of the extraction passage and extends in the axial direction of the rotating shaft, and a lubrication hole that is continuous with the internal passage and extends toward the sliding bearing. Including
3. The piston type according to claim 1, wherein the in-axis passage includes a large-diameter passage portion communicating with the lubrication hole and a small-diameter passage portion smaller in diameter than the large-diameter passage portion. Swash plate compressor. A capacity control valve that adjusts the pressure in the swash plate chamber by adjusting the opening of the air supply passage is disposed on the air supply passage.
A first throttle is formed in the extraction passage,
The first throttle is disposed downstream of the in-shaft passage in the refrigerant flow direction in the extraction passage,
A second throttle is provided downstream of the large-diameter passage portion in the in-shaft passage in the flow direction of the refrigerant,
4. The piston-type swash plate compressor according to claim 3, wherein a flow path cross-sectional area of the second throttle is larger than a flow path cross-sectional area of the first throttle.   5. The piston-type swash plate compressor according to claim 4, wherein the second diaphragm is rotatable integrally with the rotating body and is positioned at a rotation center of the rotating shaft.   The piston-type swash plate compressor according to claim 4 or 5, wherein the second throttle is provided on an attachment member attached to the in-shaft passage.

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