WO2020162101A1

WO2020162101A1 - Compressor

Info

Publication number: WO2020162101A1
Application number: PCT/JP2020/000619
Authority: WO
Inventors: 田口　幸彦
Original assignee: サンデン・オートモーティブコンポーネント株式会社
Priority date: 2019-02-06
Filing date: 2020-01-10
Publication date: 2020-08-13
Also published as: CN113272555B; JP2020125746A; JP7213709B2; CN113272555A

Abstract

[Problem] To provide a compressor capable of suitably maintaining an amount of a lubricating oil inside a crank chamber. [Solution] This compressor 100 has a configuration in which a lubricating oil flowed into an oil supply passage 147 via an inlet side opening 147A from a crank chamber 140 flows out toward one end surface 112b of a rotary body 112 from an outlet side opening 147B. The compressor 100 includes an accommodation part 148 in which an accommodating region 146c for accommodating the lubricating oil flowed out from the outlet side opening 147B is formed. In the accommodation part 148, the accommodating region 146c is formed in a radial portion corresponding to the opening position of the outlet side opening 147B on the one end surface 112b of the rotary body 112, that is, in a portion including at least an adjacent region 146c1 that is adjacent to the outer peripheral surface-side opening end of a first passage 146a. In addition, the outer peripheral surface side opening end of the first passage 146a opens to the adjacent region 146c1.

Description

Compressor

The present invention relates to a compressor in which a refrigerant sucked into a cylinder bore from a suction chamber is compressed by a reciprocating motion of a piston accompanying the rotation of a drive shaft that crosses a crank chamber and is discharged to a discharge chamber.

As an example of this type of compressor, the swash plate type compressor described in Patent Document 1 is known. This compressor has a housing having a suction chamber, a crank chamber, a discharge chamber, and a cylinder bore, a drive shaft that traverses the crank chamber, and is fixed to the drive shaft and faces one end wall portion of the housing in the crank chamber. The suction member is provided with a rotating body (lug plate) and a discharge passage (release passage) communicating between the crank chamber and the suction chamber, and reciprocating motion of a piston in the cylinder bore accompanying rotation of the drive shaft. The refrigerant sucked into the cylinder bore from the chamber is compressed and discharged into the discharge chamber. One end of the drive shaft extends in a shaft hole opened in the one end wall of the housing. A radial bearing (a plain bearing) that rotatably supports the drive shaft is provided at an opening portion of the shaft hole on the inner side of the crank chamber, and a shaft sealing device is provided at the opening portion of the shaft hole on the outer side of the crank chamber. An annular space is provided between the rotary body and one end surface of the housing, and a thrust bearing is provided between the rotary body and the one end wall portion of the housing. The discharge passage has a first passage that communicates with a region of the crank chamber that is rich in lubricating oil, and a second passage that communicates with a region of the crank chamber that is low in lubricating oil. The first passage is formed in the one end wall portion of the housing, and an oil guide passage (oil guide groove, oil guide hole) that communicates between the outer peripheral region of the crank chamber and the space, the annular space, An internal passage connected to the space and extending in the drive shaft, and a throttle hole are provided, and a region in the crank chamber rich in lubricating oil and the suction chamber communicate with each other. The internal passage includes a first hole extending in the radial direction at a predetermined angular position in the rotation direction of the drive shaft, a second hole extending in the axial direction, a communication hole, and an outflow hole. Further, the compressor increases the ratio of the first passage in the discharge passage by increasing the rotation speed of the drive shaft, and increases the proportion of the second passage in the discharge passage by decreasing the rotation speed of the drive shaft. It is configured to increase the proportion.

JP, 2009-209682, A

In the above-mentioned conventional compressor, the annular space where the first hole, which is one end of the internal passage, is opened is an area having a small volume between the shaft sealing device and the one end surface of the radial bearing. is there.

Here, the space and the first hole constitute a part of the discharge passage that communicates between the crank chamber and the suction chamber. Therefore, most of the lubricating oil that has flowed into the annular space with a small volume together with the refrigerant gas flows into the first hole together with the refrigerant gas regardless of the angular position in the rotational direction of the drive shaft, After that, the gas is discharged into the suction chamber via the internal passage including the first hole. In other words, since the first hole is directly connected to the space, the oil in the space always flows out from the first hole toward the suction chamber. As a result, for example, when the drive shaft is rotated at a high speed and a state in which a large amount of refrigerant gas containing lubricating oil in the crank chamber is continuously discharged to the suction chamber through the discharge passage, Lubricating oil in the room may be excessively reduced, which may lead to insufficient lubrication of sliding members such as the shaft sealing device.

Therefore, an object of the present invention is to provide a compressor capable of maintaining an appropriate amount of lubricating oil in the crank chamber while communicating between the crank chamber and the suction chamber.

According to one aspect of the present invention, there is provided a compressor including a housing, a drive shaft, a radial bearing, a disk-shaped rotating body, a piston, a discharge passage, and an oil supply passage. The housing has a suction chamber into which the uncompressed refrigerant is introduced, a discharge chamber, and a crank chamber. The drive shaft traverses the crank chamber, and one end thereof extends in a shaft hole opened in one end wall portion in a drive shaft extending direction of a crank chamber forming wall of the housing. The radial bearing is provided in the shaft hole and rotatably supports the drive shaft. The rotating body is fixed to the drive shaft and faces the one end wall portion in the crank chamber. The piston is housed in a cylinder bore formed in the other end wall portion of the crank chamber forming wall. The discharge passage communicates between the crank chamber and the suction chamber. The oil supply passage is a passage for guiding the lubricating oil in the crank chamber to at least the radial bearing. In the compressor, the reciprocating motion of the piston accompanying the rotation of the drive shaft compresses the refrigerant sucked from the suction chamber into the cylinder bore and discharges the compressed refrigerant to the discharge chamber. The discharge passage communicates between the crank chamber and the suction chamber via the first passage and the second passage. The first passage extends into the shaft from a predetermined angular position in the circumferential direction on the outer peripheral surface of the one end of the drive shaft. The second passage is continuous with the first passage and extends toward the other end of the drive shaft. The oil supply passage is provided in the one end wall portion and has an inlet side opening and an outlet side opening. The inlet-side opening opens in the crank chamber at a portion of the one end wall portion that is above the axis of the drive shaft in the gravity direction. The outlet side opening is a portion of the one end wall portion below the inlet side opening in the direction of gravity and at a predetermined angle around the axis of the drive shaft, and the one end surface of the one end wall portion is rotated. It opens in the crank chamber area between one end surface of the body. In the compressor, the lubricating oil that has flowed into the oil supply passage from the crank chamber through the inlet side opening flows out from the outlet side opening toward the one end surface of the rotating body. The compressor includes a receiving portion forming a receiving area for receiving the lubricating oil flowing out from the outlet side opening. The receiving portion is a portion in the radial direction corresponding to the opening position of the outlet side opening on the one end surface of the rotating body and includes at least a portion adjacent to the outer peripheral surface side opening end of the first passage. The receiving area is formed. The outer peripheral surface side opening end of the first passage opens in the adjacent region.

In the compressor according to one aspect of the present invention, the outlet side opening of the oil supply passage is a portion of the one end wall portion that is lower than the inlet side opening in the gravity direction, and has a predetermined circumference around the axis of the drive shaft. The first passage of the discharge passage extends into the shaft from a predetermined angular position in the circumferential direction on the outer peripheral surface of the one end of the drive shaft. That is, while the rotating body and the drive shaft are rotating, the angular position of the opening end of the outer peripheral surface side of the first passage provided in the drive shaft around the axis of the drive shaft changes, but The angular position of the outlet side opening that is opened in the wall is constant. Therefore, during rotation, the angular position of the outer peripheral surface side opening end of the first passage intermittently coincides with the angular position of the outlet side opening. Then, when both angular positions match, the distance between the outlet side opening and the outer peripheral surface side opening end of the first passage becomes the shortest. At this time, the oil supply passage is substantially connected to the first passage via the receiving area, and a flow of the refrigerant gas from the inlet side opening of the oil supply passage toward the outlet side opening is generated. Further, the compressor is a receiving portion that forms a receiving region for receiving the lubricating oil that has flowed out from the outlet side opening, and corresponds to an opening position of the outlet side opening on the one end surface of the rotating body. The receiving portion that forms the receiving area in a portion that is located in the radial direction and that includes the adjacent area that is adjacent to at least the outer peripheral surface side opening end of the first passage, and the receiving area is adjacent to the receiving area. In addition, the outer peripheral surface side opening end of the first passage is open. Therefore, in the compressor, whether or not the receiving area faces the outlet side opening during rotation of the rotating body, and the angular position of the outer peripheral surface side opening end of the first passage and the outlet side. Depending on the relationship with the angular position of the opening, for example, the following effects are achieved.

(1) While the rotating body is rotating, the receiving area faces the outlet side opening, and the angular position of the outer peripheral surface side opening end (adjacent area) of the first passage is the outlet side opening. When it coincides with or is close to the angular position of (period), the lubricating oil flowing out from the outlet side opening is received in the area adjacent to the receiving area. A centrifugal force associated with the rotation acts on the lubricating oil received in the adjacent region. However, the lubricating oil received in the adjacent region is a refrigerant gas that flows from the crank chamber through the inlet side opening of the oil supply passage and flows out of the outlet side opening against the centrifugal force. Flow toward the outer peripheral surface side opening end of the first passage that opens in the adjacent region, and then is discharged into the suction chamber through the first passage. (2) During the rotation of the rotating body, the receiving area faces the outlet side opening, and the angular position of the outer peripheral surface side opening end of the first passage is separated from the angular position of the outlet side opening. However, the lubricating oil flowing out from the outlet side opening is received in the receiving area when not largely separated (period). The lubricating oil received in the receiving area moves radially outward in the receiving area due to the centrifugal force associated with the rotation, and most of it temporarily stays in the receiving area. Most of the lubricating oil temporarily staying in the receiving area passes through the receiving area from the crank chamber area between the one end surface of the one end wall portion and the one end surface of the rotating body. The refrigerant gas flows toward the passage and is discharged into the suction chamber through the first passage. Further, a part of the lubricating oil temporarily retained in the receiving area does not flow into the first passage, but flows out of the receiving area by a centrifugal force, and the one end surface of the one end wall portion and the one end surface It can be stored at the bottom of the crank chamber via a crank chamber region (gap) between the one end face of the rotating body. (3) During the rotation of the rotating body, when the receiving area does not face the outlet side opening (period), the lubricating oil flowing out from the outlet side opening is applied to the one end surface of the rotating body. It collides and is stored at the bottom of the crank chamber via a crank chamber region (gap) between the one end face of the one end wall portion and the one end face of the rotating body. (4) Further, when the receiving area is formed so as to surround a wide area in the circumferential direction of the outer peripheral surface of the drive shaft, the receiving area is formed on the outlet side opening during rotation of the rotating body. There is a time (period) when they are facing each other and the angular position of the outer peripheral surface side opening end of the first passage is largely apart from the angular position of the outlet side opening. Also at this time (period), the lubricating oil received in the receiving area moves to the outside in the radial direction in the receiving area by the centrifugal force accompanying the rotation, and temporarily stays in the receiving area. However, since the angular position of the outer peripheral surface side opening end of the first passage is largely apart from the angular position of the outlet side opening, the flow of the refrigerant gas flowing out from the outlet side opening is the outer peripheral surface of the first passage. The side open end is not reached or the flow momentum is weakened. As a result, most of the lubricating oil temporarily retained in the receiving area does not flow into the first passage, but flows out of the receiving area due to centrifugal force, and the one end surface of the one end wall portion and the rotation of the one end wall portion rotate. It is stored at the bottom of the crank chamber through a crank chamber region (gap) between the one end surface of the body. Further, a part of the lubricating oil that has temporarily stayed in the receiving area may be discharged into the suction chamber via the first passage opening to the receiving area, along with the weak flow of the refrigerant gas.

That is, in the compressor according to one aspect of the present invention, during rotation of the rotating body, at a timing at which the angular position of the outer peripheral surface side opening end of the first passage substantially matches the angular position of the outlet side opening, A large amount of the lubricating oil in the crank chamber flows into the suction chamber. In other words, the compressor causes the lubricating oil in the crank chamber to intermittently flow into the suction chamber during rotation of the rotary body, or to suck the lubricating oil from the crank chamber during rotation of the rotary body. The flow rate of lubricating oil flowing into the chamber is periodically increased and decreased. In this way, by limiting the timing or period of time during which a large amount of lubricating oil flows from the crank chamber to the suction chamber, it is possible to limit the amount of lubricating oil that flows from the crank chamber to the suction chamber. As a result, the amount of lubricating oil in the crank chamber can be appropriately maintained.

In this way, it is possible to provide a compressor that can maintain an appropriate amount of lubricating oil in the crank chamber while communicating between the crank chamber and the suction chamber.

It is a schematic sectional drawing of a compressor concerning one embodiment of the present invention. It is a figure which shows typically the supply passage and discharge passage of the said compressor. FIG. 3 is a cross-sectional view of a main part including a drive shaft and a rotating body of the compressor, showing a state in which a first passage in the drive shaft is located below. FIG. 3 is a cross-sectional view of a main part including the drive shaft and the rotating body of the compressor, showing a state in which the first passage is located above. It is a rear view of the rotating body of the said compressor. It is a conceptual diagram for demonstrating the positional relationship during rotation of the receiving area|region provided in the said rotary body, and the outlet side opening of an oil supply passage. It is a figure for demonstrating the modification of the shape of the receiving area of the receiving part of the said compressor. It is a figure for demonstrating the modification of the number of the said receiving areas. It is a figure for demonstrating the modification of the formation range of the said receiving area of the said receiving part. It is a figure for demonstrating the modification of the oil supply passage of the said compressor. It is a figure for demonstrating the modification of the thrust bearing shown in FIG. It is a figure for demonstrating another modification of the said oil supply passage. It is a figure for demonstrating another modification of the oil supply passage. It is sectional drawing of the radial bearing shown in FIG. It is a perspective view of the radial bearing shown in FIG. It is a figure for demonstrating the modification of the formation mode of the said receiving area.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a sectional view of a compressor according to an embodiment of the present invention. The compressor according to the embodiment is configured as a clutchless compressor mainly applied to an air conditioner system (air conditioner system) for vehicles. In this embodiment, a case of a swash plate type variable displacement compressor with variable discharge capacity will be described as an example. The upper side in FIG. 1 is the upper side in the gravity direction when the compressor is installed, and the lower side in FIG. 1 is the lower side in the gravity direction. Similarly, the vertical relationship in the direction of gravity is also shown in FIGS. 3 to 5 and FIGS. 7 to 16 described later.

As shown in FIG. 1, the compressor 100 includes a cylinder block 101 having a plurality of cylinder bores 101 a arranged in an annular shape, a front housing 102 provided at one end of the cylinder block 101, and a cylinder block 101 at the other end. A cylinder head 104 provided via the valve plate 103.

The front housing 102, the center gasket (not shown), the cylinder block 101, the cylinder gasket 152, the intake valve forming plate 150, the valve plate 103, the discharge valve forming plate 151, the head gasket 153, and the cylinder head 104 are sequentially connected, The housing of the compressor 100 is formed by being fastened by the through bolts 105. A crank chamber 140 (control pressure chamber) is formed by the cylinder block 101 and the front housing 102, and a drive shaft 110 extending in the horizontal direction is provided across the crank chamber 140. The front housing 102 is formed in a cylindrical shape with a bottom, has a substantially cylindrical peripheral wall 102a and one end wall portion 102b that closes one end of the peripheral wall 102a, and the opening at the other end of the peripheral wall 102a is closed by the cylinder block 101. ing. The cylinder bore 101a is formed in the cylinder block 101. In the present embodiment, the cylinder block 101 and the front housing 102 correspond to the "crank chamber forming wall" of the present invention, and the one end wall portion 102b of the front housing 102 corresponds to the "crank chamber forming wall of the housing" of the present invention. In the drive shaft extending direction", and the cylinder block 101 corresponds to the "other end wall portion of the crank chamber forming wall" according to the present invention.

A swash plate 111 is arranged around the axially intermediate portion of the drive shaft 110. The swash plate 111 is connected to a disc-shaped rotating body 112 fixed to the drive shaft 110 via a link mechanism 120, and rotates together with the drive shaft 110. Further, the swash plate 111 is configured such that an angle (an inclination angle of the swash plate 111) with respect to a plane orthogonal to the axis O of the drive shaft 110 can be changed. The rotating body 112 faces the one end wall portion 102b of the front housing 102 in the crank chamber 140. On the end surface of the rotating body 112 on the side of the one end wall portion 102b, an annular projecting portion 112c having a substantially trapezoidal cross-sectional shape is provided so as to project toward the one end wall portion 102b side. A thrust bearing 133 described later is attached to the outer periphery of the protruding portion 112c. A gap (corresponding to a crank chamber area 140a described below) is provided between the one end surface 102b1 of the one end wall portion 102b of the front housing 102 and the one end surface 112b of the rotating body 112 that face each other. Specifically, the one end surface 112b of the rotating body 112 is a portion of the end surface of the rotating body 112 on the one end wall portion 102b side between the inner wall surface of the annular projecting portion 112c and the outer peripheral surface of the drive shaft 110. Is.

The link mechanism 120 includes a first arm 112a protruding from the rotating body 112, a second arm 111a protruding from the swash plate 111, and one end side with respect to the first arm 112a via the first connecting pin 122. The link arm 121 is rotatably connected and the other end side is rotatably connected to the second arm 111a via the second connecting pin 123.

The through hole 111b of the swash plate 111, through which the drive shaft 110 is inserted, is formed in a shape that allows the swash plate 111 to tilt within a range between the maximum tilt angle and the minimum tilt angle. The through hole 111b is formed with a minimum tilt angle restricting portion that comes into contact with the drive shaft 110. When the inclination angle of the swash plate 111 when the swash plate 111 is orthogonal to the axis O of the drive shaft 110 is 0°, the minimum inclination angle restricting portion of the through hole 111b is such that the inclination angle of the swash plate 111 is approximately 0°. It is formed so as to come into contact with the drive shaft 110 and to restrict further tilting of the swash plate 111. When the tilt angle of the swash plate 111 reaches the maximum tilt angle, the swash plate 111 contacts the rotating body 112 and further tilting is restricted.

On the drive shaft 110, a tilt reducing spring 114 that biases the swash plate 111 in a direction that decreases the tilt angle of the swash plate 111, and a tilt increasing spring 115 that biases the swash plate 111 in a direction that increases the tilt angle of the swash plate 111. And are installed. The tilt angle reducing spring 114 is arranged between the swash plate 111 and the rotating body 112, and the tilt angle increasing spring 115 is mounted between the swash plate 111 and the spring support member 116 fixed to the drive shaft 110.

Here, when the tilt angle of the swash plate 111 is the minimum tilt angle, the biasing force of the tilt angle increasing spring 115 is set to be larger than the biasing force of the tilt angle decreasing spring 114, and the drive shaft 110 is rotating. When not present, the swash plate 111 is positioned at an inclination angle that balances the biasing force of the tilt angle decreasing spring 114 and the biasing force of the tilt angle increasing spring 115.

One end portion (left end side in FIG. 1) of the drive shaft 110 extends in the shaft hole 102d opened in the one end wall portion 102b of the front housing 102 and extends to the outside of the front housing 102. Specifically, the shaft hole 102d penetrates through the inside of the protruding portion 102c that partially protrudes outward at the radial center portion of the one end wall portion 102b of the front housing 102. A power transmission device (not shown) is connected to the one end of the drive shaft 110. Rotational power of the drive shaft 110 is input from an external power source via the power transmission device. The inside of the crank chamber 140 is shielded from the external space by the shaft sealing device 130 provided on the protrusion 102c. A first bearing 131 that rotatably supports the drive shaft 110 is provided in the shaft hole 102d (specifically, an opening portion of the shaft hole 102d on the crank chamber inner side). The shaft sealing device 130 is provided in a region outside the crank chamber of the shaft hole 102d with an annular space W between the one end face 131a in the axial direction of the first bearing 131, and the outer peripheral surface of the drive shaft 110 and the shaft. The inner peripheral surface of the hole 102d is hermetically sealed. The first bearing 131 in the present embodiment corresponds to the “radial bearing” according to the present invention.

The other end (right end side in FIG. 1) of the drive shaft 110 is inserted through a center bore 101b formed in the cylinder block 101. The center bore 101b penetrates the cylinder block 101 at the center of the plurality of cylinder bores 101a, and has a large diameter portion that opens from the valve plate 103 side toward the crank chamber 140 side to the end surface of the cylinder block 101 on the cylinder head 104 side. 101b1, a small-diameter medium-diameter portion 101b2 smaller than the large-diameter portion 101b1, and a small-diameter portion 101b3 smaller than the medium-diameter portion 101b2. The other end of the drive shaft 110 is rotatably supported by a second bearing 132 provided on the small diameter portion 101b3 of the center bore 101b.

The coupling body including the drive shaft 110 and the rotating body 112 fixed to the drive shaft 110 is supported by the first bearing 131 and the second bearing 132 in the radial direction, and is supported by the thrust bearing 133 in the thrust direction. .. In this embodiment, the first bearing 131 and the second bearing 132 are slide bearings. The thrust bearing 133 is sandwiched between the rotating body 112 and the one end wall portion 102b of the front housing 102 while being attached to the outer peripheral surface of the protruding portion 112c of the rotating body 112, and the thrust direction load acting on the rotating body 112. Is to support. The drive shaft 110 is configured to rotate in synchronization with the rotation of the power transmission device by transmitting the power from the external drive source to the power transmission device.

A piston 136 is housed in each cylinder bore 101a. An outer space of the swash plate 111 and the vicinity thereof are housed in an inner space formed in a protruding portion of the piston 136 that projects into the crank chamber 140. The swash plate 111 includes the piston 136 through a pair of shoes 137. It is configured to work with. Then, the rotation of the swash plate 111 accompanying the rotation of the drive shaft 110 causes each piston 136 to reciprocate within the corresponding cylinder bore 101a.

The cylinder head 104 is divided into a suction chamber 141 arranged in the center and a discharge chamber 142 surrounding the suction chamber 141 in an annular shape. That is, the housing of the compressor 100 has the suction chamber 141, the discharge chamber 142, and the crank chamber 140. The suction chamber 141 and each cylinder bore 101a communicate with each other through a communication hole 103a provided in the valve plate 103 and a suction valve (not shown) formed in the suction valve forming plate 150. The discharge chamber 142 and each cylinder bore 101a communicate with each other through a communication hole 103b provided in the valve plate 103 and a discharge valve (not shown) formed in the discharge valve forming plate 151. A discharge check valve 200 is arranged in the discharge chamber 142.

The low-pressure side refrigerant (that is, the refrigerant before compression) of the refrigerant circuit of the air conditioner system is introduced into the intake chamber 141 via the intake port 106 and the intake passage 107. The refrigerant in the suction chamber 141 is sucked into the corresponding cylinder bore 101a by the reciprocating motion of each piston 136, compressed, and discharged into the discharge chamber 142. That is, the reciprocating motion of the piston 136 accompanying the rotation of the drive shaft 110 compresses the refrigerant sucked into the cylinder bore 101 a from the suction chamber 141 and discharges it to the discharge chamber 142. The cylinder bore 101a and the piston 136 constitute a compression unit that sucks and compresses the refrigerant in the suction chamber 141. Then, the refrigerant discharged to the discharge chamber 142 is guided to the high pressure side of the refrigerant circuit of the air conditioner system via the discharge passage 108 and the discharge port 109. Further, the discharge check valve 200 blocks the reverse flow of the refrigerant (refrigerant gas) from the high pressure side of the refrigerant circuit of the air conditioner system toward the discharge chamber 142.

In the present embodiment, the compressor 100 includes a supply passage 145 for supplying the refrigerant in the discharge chamber 142 to the crank chamber 140, and a discharge passage 146 for discharging the refrigerant in the crank chamber 140 to the suction chamber 141. have. FIG. 2 is a diagram schematically showing the supply passage 145 and the discharge passage 146.

As shown in FIG. 2, the supply passage 145 is formed as a passage that communicates between the discharge chamber 142 and the crank chamber 140, and the control valve 300 is provided in the middle of the supply passage 145. The control valve 300 is configured to adjust the opening degree (passage cross-sectional area) of the supply passage 145 and thereby control the supply amount of the refrigerant (discharge refrigerant) in the discharge chamber 142 to the crank chamber 140. ..

The discharge passage 146 is formed as a passage that communicates between the crank chamber 140 and the suction chamber 141, and has a throttle portion (a throttle passage 103c described later).

The control valve 300 includes a valve unit and a drive unit (solenoid) that opens and closes the valve unit, and introduces the suction chamber 141 through a communication passage 104b (see FIG. 1) formed in the cylinder head 104. The opening degree of the supply passage 145 is controlled in response to the pressure and the electromagnetic force generated by the current flowing through the solenoid in response to the external signal. Specifically, the coil of the drive unit is connected to a control device (not shown) provided outside the compressor 100 via a signal line or the like. The drive unit generates an electromagnetic force F(I) when the control current I is supplied to the coil from the controller. When the drive unit generates an electromagnetic force F(I), the valve body of the valve unit moves in the valve closing direction. Further, when the pressure in the suction chamber 141 becomes higher than the set pressure set by the control current I, the valve body increases the discharge capacity by increasing the opening of the valve hole (that is, the supply passage 145) (passage cross-sectional area). ) Is reduced to lower the pressure in the crank chamber 140, and when the pressure in the suction chamber 141 falls below the set pressure, the opening of the valve hole (that is, the supply passage 145) is increased in order to reduce the discharge capacity. Then, the pressure in the crank chamber 140 is increased. That is, the control valve 300 autonomously controls the opening degree of the supply passage 145 so that the pressure in the suction chamber 141 approaches the set pressure. Since the electromagnetic force of the drive unit acts on the valve body in the valve closing direction, when the energization amount of the coil increases, the force in the direction of decreasing the opening degree of the supply passage 145 (that is, the valve closing direction) increases. However, the set pressure changes so as to decrease. The control device controls energization to the coil of the drive unit by pulse width modulation (PWM control) at a predetermined frequency in the range of 400 Hz to 500 Hz, for example, so that the current value flowing through the coil becomes a desired value. Change the pulse width (duty ratio).

When the control valve 300 is closed, the communication between the discharge chamber 142 and the crank chamber 140 is cut off, the refrigerant in the crank chamber 140 is discharged to the suction chamber 141 via the discharge passage 146, and the pressure in the crank chamber 140 is reduced. .. When the pressure in the crank chamber 140 decreases, the inclination angle of the swash plate 111 increases, and the stroke of the piston 136 (that is, the discharge capacity of the compressor 100) also increases.

On the other hand, when the control valve 300 is opened, the discharge chamber 142 and the crank chamber 140 are communicated with each other, and the refrigerant in the discharge chamber 142 is guided into the crank chamber 140 via the supply passage 145. At this time, the crank chamber 140 and the suction chamber 141 communicate with each other through the discharge passage 146, but since the discharge passage 146 has the throttle portion, the refrigerant in the crank chamber 140 is discharged to the suction chamber 141. As a result, the pressure in the crank chamber 140 increases. Then, the refrigerant in the discharge chamber 142 is supplied to the crank chamber 140 via the supply passage 145 according to the opening degree of the supply passage 145 by the control valve 300, and the pressure of the crank chamber 140 rises. When the pressure in the crank chamber 140 increases, the inclination angle of the swash plate 111 decreases and the stroke of the piston 136 (that is, the discharge capacity of the compressor 100) also decreases.

As described above, in the compressor 100, the refrigerant in the discharge chamber 142 is supplied to the crank chamber 140 via the supply passage 145, and the refrigerant in the crank chamber 140 is discharged to the suction chamber 141 via the discharge passage 146. As a result, the pressure in the crank chamber 140 is adjusted, whereby the discharge capacity is changed.

Lubricating oil for lubricating the sliding surfaces of the shaft sealing device 130, the bearings (131, 132, 133), and the sliding members such as the swash plate 111 is mainly stored in the crank chamber 140. ing. The lubricating oil in the crank chamber 140 is stored below the crank chamber 140 in the direction of gravity when the drive shaft 110 stops rotating. When the drive shaft 110 rotates, the lubricating oil in the crank chamber 140 is agitated as the drive shaft 110 rotates, and the region on the peripheral wall 102a side in the crank chamber 140 becomes a region with a large amount of lubricating oil. The region on the radial center side (drive shaft 110 side) in the chamber 140 is a region in which the content of lubricating oil is small.

3 and 4 are cross-sectional views of a main part including the drive shaft 110 and the rotating body 112 of the compressor 100, and FIG. 4 is a state in which the drive shaft 110 and the rotating body 112 are rotated by 180° from the state shown in FIG. It is shown. It should be noted that FIG. 3 shows a state in which a later-described first passage 146a formed in the drive shaft 110 is located below, and FIG. 4 shows a state in which the first passage 146a is located above.

The compressor 100 includes an oil supply passage 147 for guiding the lubricating oil in the crank chamber 140 to at least the first bearing 131. The oil supply passage 147 is provided in the one end wall portion 102b of the front housing 102, and has an inlet side opening 147A and an outlet side opening 147B. The lubricating oil that has flowed into the oil supply passage 147 from the crank chamber 140 through the inlet side opening 147A flows out from the outlet side opening 147B toward the one end surface 112b of the rotating body 112. A part of the lubricating oil in the crank chamber 140 is discharged to the suction chamber 141 through the discharge passage 146 as the refrigerant moves, and then sucked into the cylinder bore 101a to slide the piston 136 or the like. It is supplied to members and the like. That is, the lubricating oil is stirred as the drive shaft 110 rotates, and the lubricating oil moves as the refrigerant moves through the oil supply passage 147 and the discharge passage 146, thereby lubricating the inside of the compressor 100. ..

The compressor 100 also includes a receiving portion 148 that forms a receiving region 146c for receiving the lubricating oil that has flowed out from the outlet side opening 147B of the oil supply passage 147. In the present embodiment, the receiving area 146c is formed as a recessed area in the one end surface 112b of the rotating body 112. That is, the receiving area 146c is open to the crank chamber area 140a between the one end surface 102b1 of the one end wall portion 102b of the front housing 102 and the one end surface 112b of the rotating body 112. The crank chamber region 140a is a region formed by a gap between the one end face 102b1 of the one end wall portion 102b and the one end face 112b of the rotating body 112, and is a part of the region in the crank chamber 140.

In the following, the supply passage 145, the discharge passage 146, the oil supply passage 147, and the receiving portion 148 will be described in detail.

"Supply passage 145"
When the control valve 300 is opened, the discharge chamber 142 and the crank chamber 140 communicate with each other through the supply passage 145, and the refrigerant in the discharge chamber 142 is supplied to the crank chamber 140 via the supply passage 145. As shown in FIG. 1, in the present embodiment, the supply passage 145 is formed by a communication passage 104c formed in the cylinder head 104, a passage in the control valve 300, a communication passage 104d extending in the cylinder head 104 and the cylinder block 101. ing.

"Discharge passage 146"
The discharge passage 146 communicates between the crank chamber 140 and the suction chamber 141 via the first passage 146a and the second passage 146b. The first passage 146a extends into the shaft from a predetermined angular position in the circumferential direction on the outer peripheral surface of the one end (the left side in FIG. 1, the end on the shaft sealing device 130 side) of the drive shaft 110. The second passage 146b is continuous with the first passage 146a and extends to the other end portion side (the right side in FIG. 1, the cylinder head 104 side) of the drive shaft 110. For example, the first passage 146a extends radially from the outer peripheral surface of the drive shaft 110 at a predetermined angular position in the peripheral direction on the outer peripheral surface. The second passage 146b extends from the shaft inner end of the first passage 146a along the axis O so as to penetrate the end surface of the drive shaft 110 on the other end side. An outer peripheral surface side opening end of the first passage 146a is open to a receiving region 146c (specifically, an adjacent region 146c1 described later) formed by the receiving portion 148. The receiving area 146c is open to the crank chamber area 140a which is a part of the crank chamber 140. Therefore, the first passage 146a communicates with the crank chamber 140 via the receiving area 146c. That is, the receiving area 146c constitutes an opening end of the discharge passage 146 on the crank chamber 140 side. In the present embodiment, the discharge passage 146 that communicates between the crank chamber 140 and the suction chamber 141 has a receiving area 146c, a first passage 146a, a second passage 146b, a medium diameter portion 101b2, and a large diameter portion 101b1. And a throttle passage (fixed throttle) 103c formed in the valve plate 103 (see FIG. 1). In the discharge passage 146, the flow passage cross-sectional area of the first passage 146a is set smaller than the flow passage cross-sectional area of the second passage 146b and larger than the flow passage cross-sectional area of the throttle passage 103c.

"Oil supply passage 147"
As described above, the oil supply passage 147 is provided in the one end wall portion 102b of the front housing 102 and has the inlet side opening 147A and the outlet side opening 147B. The inlet-side opening 147A opens into the crank chamber 140 at a portion of the one end wall portion 102b (one end surface 102b1) above the axis O of the drive shaft 110 in the gravity direction. The outlet side opening 147B is a portion of the one end wall portion 102b (one end surface 102b1) below the inlet side opening 147A in the direction of gravity and at a predetermined angle around the axis O of the drive shaft 110 in the crank chamber region 140a. Open. In the present embodiment, the oil supply passage 147 extends via the annular space W between the shaft sealing device 130 and the first bearing 131, and has an inlet side oil passage 147a having an inlet side opening 147A, An outlet side oil passage 147b having an outlet side opening 147B is included. That is, the oil supply passage 147 includes the inlet side oil passage 147a, the space W, and the outlet side oil passage 147b. Most of the lubricating oil guided from the crank chamber 140 to the annular space W via the inlet side oil passage 147a flows out from the space W via the outlet side oil passage 147b.

The inlet-side oil passage 147a has one end serving as the inlet-side opening 147A, which opens to the crank chamber 140 at a portion of the one-end wall portion 102b that is above the drive shaft 110 in the direction of gravity and radially outside of the thrust bearing 133, and the other end is open. It opens in the upper region in the annular space W. The inlet oil passage 147a is formed by, for example, an oil guide groove portion 147a1, an oil guide hole 147a2, and an end surface of the thrust bearing 133 on the one end wall portion 102b side. The oil guide groove portion 147a1 is a groove that extends downward from a portion of the one end wall portion 102b above the outer edge portion of the thrust bearing 133, and extends downward along the one end surface 102b1 of the one end wall portion 102b. The lower side portion of the oil guide groove portion 147a1 is closed by the end face plate 133a on the one end wall portion 102b side of the thrust bearing 133, and the upper side portion of the oil guide groove portion 147a1 is opened to the crank chamber 140, An inlet side opening 147A of the supply passage 147 is configured. The oil guide hole 147a2 extends obliquely from the lower end portion of the oil guide groove portion 147a1 into the one end wall portion 102b, and opens in the upper region of the annular space W. When the drive shaft 110 rotates, the lubricating oil in the crank chamber 140 is agitated, and the region on the peripheral wall 102a side in the crank chamber 140 becomes a region with a large amount of lubricating oil. The lubricating oil in the region on the peripheral wall 102a side in the crank chamber 140 is mainly supplied to the shaft sealing device 130 and the first bearing 131 via the oil passage 147a on the inlet side of the oil supply passage 147. Lubricating oil flows into the gap in the thrust bearing 133 from the radially outer edge portion of the thrust bearing 133.

The outlet-side oil passage 147b has one end opening to a lower region in the annular space W, and the other end as the outlet-side opening 147B is below the drive shaft 110 in the one end wall portion 102b in the gravity direction and has a diameter of the thrust bearing 133. An opening is made in the crank chamber region 140a at a portion inside the inner edge in the direction. The outlet-side oil passage 147b extends obliquely downward from the one end toward the rotary body 112 side, and then bends toward the axis O of the drive shaft 110 and extends parallel to the axis O. For example, the outlet side opening 147B (the other end) of the outlet side oil passage 147b is opened at an angular position shifted by 180° around the axis O of the drive shaft 110 with respect to the opening angular position of the inlet side opening 147A. The one end of the oil passage 147b is opened at an angular position shifted by 180° around the axis O of the drive shaft 110 with respect to the angular position of the opening of the other end of the inlet-side oil passage 147a.

In this embodiment, as described above, the first bearing 131 is a slide bearing. Therefore, a minute gap, that is, a face-to-face gap, exists between the inner peripheral surface of the first bearing 131 and the outer peripheral surface of the drive shaft 110. Therefore, the lubricating oil that has flowed into the space W from the crank chamber 140 via the inlet-side oil passage 147a of the oil supply passage 147 flows out through the inter-face clearance between the first bearing 131 and the drive shaft 110. obtain. However, since the flow passage cross-sectional area of the oil supply passage 147 is sufficiently larger than the area between the surface gaps, most of the lubricating oil that has flowed into the space W exits via the outlet-side oil passage 147b of the oil supply passage 147. It flows out from the side opening 147B toward the one end surface 112b of the rotating body 112.

"Receptor 148"
The receiving portion 148 forms a receiving area 146c for receiving the lubricating oil flowing out from the outlet side opening 147B. The receiving region 146c is a portion in the radial direction corresponding to the opening position of the outlet side opening 147B on the one end surface 112b of the rotating body 112, and at least the adjacent region 146c1 adjacent to the outer peripheral surface side opening end of the first passage 146a. It is formed in the part containing. That is, the receiving portion 148 is a forming wall that forms the receiving region 146c, and is a part of the rotating body 112 on the side of the one end surface 112b.

FIG. 5 is a rear view of the rotating body 112 viewed from the one end wall portion 102b side. As shown in FIGS. 1 and 3 to 5, in the present embodiment, as described above, the receiving area 146c is formed as a recessed area on the one end surface 112b (a part of the back surface) of the rotating body 112. There is. Specifically, the receiving area 146c is one of the portions (that is, one end surface 112b) between the inner wall surface of the annular projecting portion 112c and the outer peripheral surface of the drive shaft 110 on the end surface on the one end wall portion 102b side of the rotating body 112. Is formed as a recessed region.

Further, in the present embodiment, the receiving area 146c is formed so as to partially surround the outer peripheral surface of the drive shaft 110 in the circumferential direction. Specifically, a fitting hole for the drive shaft 110 is opened in the radial center of the rotating body 112, and a part of the outer edge of the opening on the one end face 112b side in the fitting hole in the circumferential direction is formed. It is partially widened to be larger than the outer diameter of the drive shaft 110. This partially widened portion constitutes the receiving area 146c. In the present embodiment, the adjacent region 146c1 adjacent to the outer peripheral surface side opening end of the first passage 146a is located in the end region of the receiving region 146c opposite to the rotation direction R of the rotating body 112. Therefore, the outer peripheral surface side opening end of the first passage 146a is opened in the end region of the receiving region 146c opposite to the rotation direction R of the rotating body 112. The receiving region 146c has a circumferential width of a predetermined angle (generally 90° in FIG. 5) in the circumferential direction of the rotating body 112 with respect to the first passage 146a, and also has a predetermined radial direction in the radial direction of the rotating body 112. Has a width. The receiving area 146c is formed as an arc groove-shaped space extending in the circumferential direction of the outer peripheral surface of the drive shaft 110 as a whole. That is, the receiving portion 148 cooperates with the outer peripheral surface of the drive shaft 110 to form an arcuate groove-shaped opening that opens to the crank chamber region 140a on the one end surface 112b of the rotating body 112.

As shown in FIGS. 3 to 5, the receiving portion 148 forming the receiving region 146c has a peripheral wall surface 148a of the enlarged diameter portion of the fitting hole and a bottom wall surface 148b.

In the present embodiment, the peripheral wall surface 148a includes the facing surface 148a1 facing the outer peripheral surface side opening end of the first passage 146a, and further extends from the facing surface 148a1 in the rotation direction R of the rotating body 112. In the present embodiment, the peripheral wall surface 148a has a constant radius of curvature centered on the axis O of the drive shaft 110, and extends in an arc surface facing the outer peripheral surface of the drive shaft 110. The radius of curvature of the peripheral wall surface 148a is set to be larger than the radius of the drive shaft 110 and smaller than the radius of the radially inner edge portion of the thrust bearing 133. The radius of curvature of the peripheral wall surface 148a is set to be slightly larger than the distance from the axis O of the drive shaft 110 to the lower end of the outlet side opening 147B of the oil supply passage 147 in the vertical direction (FIG. 3). reference). The bottom wall surface 148b is the bottom surface of the receiving area 146c that is recessed from the other portion of the one end surface 112b at the radial portion corresponding to the opening position of the outlet side opening 147B in the one end surface 112b of the rotating body 112, and the first bearing It faces the other end surface 131 b of 131. The bottom wall surface 148b faces the outlet side opening 147B as shown in FIG. 3 or does not face the outlet side opening 147B as shown in FIG. 4 while the rotor 112 is rotating. The outlet-side opening 147B is covered with the peripheral wall surface 148a and the bottom wall surface 148b of the receiving portion 148 in the state shown in FIG. 3, and is covered with the one end surface 112b of the rotating body 112 in the state shown in FIG. The gap between the one end surface 102b1 of the one end wall portion 102b and the one end surface 112b of the rotating body 112 (the crank chamber area 140a) is preferably set small, for example, a predetermined value in the range of 0.5 mm to 3 mm. Is set to.

Next, the operation of the compressor 100 according to the present embodiment will be described with reference to FIGS. 3, 4 and 6 regarding the flow of lubricating oil in the crank chamber 140. FIG. 6 is a conceptual diagram for explaining the positional relationship between the receiving area 146c and the outlet side opening 147B of the oil supply passage 147 during rotation. Although the absolute position of the outlet side opening 147B is fixed and constant, when viewed from the rotating body 112 during the rotation of the rotating body 112, the angular position of the outlet side opening 147B with respect to the first passage 146a changes. The state of change of the angular position of the outlet side opening 147B viewed from the rotating body 112 is represented by a circle shown by a dotted line in FIG.

As shown in FIGS. 3 and 4, in the compressor 100, while the rotating body 112 and the drive shaft 110 are rotating, about the axis O of the outer peripheral surface side opening end of the first passage 146 a provided in the drive shaft 110. However, the angular position of the outlet side opening 147B opened in the one end wall portion 102b of the front housing 102 is constant. Therefore, during rotation, the angular position of the outer peripheral surface side opening end of the first passage 146a intermittently coincides with the angular position of the outlet side opening 147B. When these two angular positions match, the distance between the outlet side opening 147B and the outer peripheral surface side opening end of the first passage 146a becomes the shortest. At this time, the oil supply passage 147 is substantially connected to the first passage 146a via the receiving area 146c, and the flow of the refrigerant gas from the inlet side opening 147A of the oil supply passage 147 toward the outlet side opening 147B is generated. Specifically, when the compressor 100 operates and the drive shaft 110 rotates, the lubricating oil in the crank chamber 140 is agitated and scattered around. Then, the scattered lubricating oil adheres to the one end surface 102b1 of the one end wall portion 102b. The lubricating oil attached to the upper portion of the one end surface 102b1 in the direction of gravity flows from the inlet side opening 147A of the oil supply passage 147 and flows into the space W via the inlet side oil passage 147a. The lubricating oil that has flowed into the space W flows through the outlet-side oil passage 147b and flows out from the outlet-side opening 147B toward the one end surface 112b of the rotating body 112. In the compressor 100, whether or not the receiving area 146c faces the outlet side opening 147B while the rotating body 112 is rotating, and the angular position of the outer peripheral surface side opening end of the first passage 146a and the outlet side opening. Depending on the relationship with the angular position of 147B, for example, the following actions (1) to (3) are achieved.

In the compressor 100, (1) as indicated by a double-headed arrow A in FIG. 6, the receiving area 146c faces the outlet side opening 147B while the rotating body 112 is rotating, and the outer peripheral surface of the first passage 146a. When the angular position of the side opening end (adjacent region 146c1) coincides with or is close to the angular position of the outlet side opening 147B (period), the lubricating oil flowing out from the outlet side opening 147B collides with the bottom wall surface 148b of the adjacent region 146c1. Acceptable. A centrifugal force associated with the rotation acts on the lubricating oil received in the adjacent region 146c1. However, the lubricating oil received in the adjacent region 146c1 resists the centrifugal force and flows in from the crank chamber 140 via the inlet side opening 147A of the oil supply passage 147 and flows out from the outlet side opening 147B. Flow vigorously toward the open end on the outer peripheral surface side of the first passage 146a opening in the adjacent region 146c1, and then discharged into the suction chamber 141 via the first passage 146a. (2) As indicated by a double-headed arrow B in FIG. 6, the receiving region 146c faces the outlet side opening 147B while the rotating body 112 is rotating, and the angle of the outer peripheral surface side opening end of the first passage 146a is increased. When the position is apart from the angular position of the outlet side opening 147B but is not largely apart (period), the lubricating oil flowing out from the outlet side opening 147B is received in the receiving area 146c. The lubricating oil received in the receiving area 146c moves radially outward in the receiving area 146c due to the centrifugal force associated with the rotation, and most of it temporarily stays in the receiving area 146c. Most of the lubricating oil temporarily retained in the receiving area 146c passes through the receiving area 146c from the crank chamber area 140a between the one end surface 102b1 of the one end wall portion 102b and the one end surface 112b of the rotating body 112. The refrigerant gas flows toward the first passage 146a and is discharged into the suction chamber 141 through the first passage 146a opening to the receiving area 146c. Further, a part of the lubricating oil temporarily staying in the receiving area 146c does not flow into the first passage 146a, but flows out of the receiving area 146c by the centrifugal force, and the one end surface 102b1 of the one end wall portion 102b is removed. It can be stored in the bottom of the crank chamber 140 via a crank chamber region 140a between the one end surface 112b of the rotating body 112 and the crank chamber 140. On the other hand, (3) as indicated by a double-headed arrow C in FIG. 6, while the rotating body 112 is rotating, when the receiving area 146c does not directly face the outlet side opening 147B (period), it flows out from the outlet side opening 147B. The lubricating oil collides with the one end surface 112b of the rotating body 112 and is stored in the bottom of the crank chamber 140 via the crank chamber area 140a between the one end surface 102b1 of the one end wall portion 102b and the one end surface 112b of the rotating body 112. To be done.

That is, in the compressor 100, during rotation of the rotating body 112, the lubrication in the crank chamber 140 is performed at the timing when the angular position of the outer peripheral surface side opening end of the first passage 146a substantially matches the angular position of the outlet side opening 147B. A large amount of oil is made to flow into the suction chamber 141. In other words, in the compressor 100, the lubricating oil in the crank chamber 140 is intermittently discharged to the suction chamber 141 while the rotating body 112 is rotating, or the compressor 100 is sucking from the crank chamber 140 while the rotating body 112 is rotating. The flow rate of lubricating oil flowing out to 141 is periodically increased and decreased. Thus, by limiting the timing or period during which a large amount of lubricating oil flows from the crank chamber 140 to the suction chamber 141, it is possible to limit the amount of lubricating oil that flows from the crank chamber 140 to the suction chamber 141. As a result, the amount of lubricating oil in the crank chamber 140 can be appropriately maintained.

In this way, it is possible to provide the compressor 100 capable of maintaining an appropriate amount of lubricating oil in the crank chamber 140 while communicating between the crank chamber 140 and the suction chamber 141.

Although the discharge of a large amount of lubricating oil from the crank chamber 140 is limited in this way, for example, a suitable amount (a small amount) of lubricating oil is discharged to the suction chamber 141 in order to supply the lubricating oil to the piston 136 and the like. There is a need. In this regard, in the present embodiment, the receiving portion 148 has the peripheral wall surface 148a including the facing surface 148a1 facing the opening end on the outer peripheral surface side of the first passage 146a. As a result, it is possible to effectively prevent or suppress the lubricating oil received in the receiving area 146c from scattering to the outside of the receiving area 146c due to the centrifugal force. As a result, the lubricating oil flowing out from the outlet side opening 147B of the oil supply passage 147 can be reliably received in the receiving area 146c and discharged to the suction chamber 141.

In the present embodiment, the peripheral wall surface 148a further extends from the facing surface 148a1 in the rotation direction R of the rotating body 112. With this, the area of the receiving area 146c can be expanded in the circumferential direction only by appropriately setting the circumferential width of the circumferential wall surface 148a, and the circumferential width of the receiving area 146c can be adjusted. As a result, the amount of lubricating oil flowing into the first passage 146a can be easily adjusted. In other words, by adjusting the circumferential width of the peripheral wall surface 148a, it is possible to adjust the ratio of the amount of lubricating oil that flows into the suction chamber 141 and the amount of lubricating oil that returns to the crank chamber 140. In the present embodiment, as shown in FIG. 5, the circumferential width of the receiving area 146c is approximately 90°, but this circumferential width (angle) can be set appropriately. When the circumferential width of the receiving area 146c is narrowed, the amount of lubricating oil returned to the crank chamber 140 decreases.

In the present embodiment, the adjacent region 146c1 is located in the end region of the receiving region 146c on the opposite side of the rotation direction R of the rotating body 112. That is, the outer peripheral surface side opening end of the first passage 146a is opened in the end region of the receiving region 146c opposite to the rotation direction R of the rotating body 112. As a result, the lubricating oil received and retained in the receiving area 146c can be effectively guided to the first passage 146a.

In the present embodiment, the receiving area 146c is formed as a recessed area in the one end surface 112b of the rotating body 112. As a result, it is possible to effectively prevent or suppress the lubricating oil received in the receiving area 146c from scattering outside the receiving area 146c.

In the present embodiment, the receiving area 146c is formed so as to partially surround the outer peripheral surface of the drive shaft 110 in the circumferential direction. Accordingly, a period during which the outlet side opening 147B of the oil supply passage 147 is not directly facing the receiving area 146c and is substantially closed by the one end surface 112b of the rotating body 112 can be provided during the rotation of the rotating body 112. As a result, the amount of lubricating oil flowing from the crank chamber 140 to the suction chamber 141 can be significantly reduced.

In the following, some modified examples of the compressor 100 according to the present embodiment will be described with reference to FIGS. 6 to 11. 7 to 16 are views for explaining modified examples of the compressor 100, respectively.

FIG. 7 is a diagram for explaining a modification of the shape of the receiving area 146c of the receiving portion 148. In the present embodiment, the peripheral wall surface 148a of the receiving portion 148 is assumed to extend with a constant radius of curvature about the axis O of the drive shaft 110, and the radial width of the rotating body 112 in the receiving region 146c. Is assumed to be constant, but is not limited to this. For example, the radial width of the rotating body 112 of the receiving region 146c may be formed so as to become narrower toward the end region (adjacent region 146a1 in FIG. 7) in the circumferential direction of the rotating body 112. As a result, the lubricating oil received and retained in the receiving area 146c can be more effectively guided to the first passage 146a.

FIG. 8 is a diagram for explaining a modified example of the number of receiving areas 146c. In the present embodiment, the number of the receiving region 146c is one, but the number is not limited to this, and may be two or more (two in the figure) as shown in FIG. In this case, the first passages 146a are formed at a plurality of angular positions offset in the circumferential direction on the outer peripheral surface of the drive shaft 110, and the receiving regions 146c are formed corresponding to the plurality of first passages 146a, respectively. .. Thereby, the number of times that the angular position of the outer peripheral surface side opening end of the first passage 146a around the axis O is coincident with the angular position of the outlet side opening 147B around the axis O during one rotation of the rotating body 112 is increased. You can As a result, it is possible to provide a plurality of times or periods during which a large amount of lubricating oil flows from the crank chamber 140 to the suction chamber 141 during one rotation of the rotating body 112.

FIG. 9 is a diagram for explaining a modification of the formation range of the receiving area 146c. In the present embodiment, the receiving area 146c is formed so as to partially surround the outer peripheral surface of the drive shaft 110 in the circumferential direction, but the present invention is not limited to this. For example, as shown in FIG. 9, the receiving region 146c may be annularly provided so as to surround the entire outer peripheral surface of the drive shaft 110. In this case, the receiving portion 148 cooperates with the outer peripheral surface of the drive shaft 110 to form an annular opening on the one end surface 112b of the rotating body 112 that opens to the crank chamber area 140a. When the receiving area 146c is provided in an annular shape, the receiving area 146c faces the outlet side opening 147B even in the period shown by the double-headed arrow C in FIG. In this modified example, the compressor 100 has the same operation as the above-described (1) and (2) in the period shown by the double-headed arrows A and B in FIG. 6, but is shown by the double-headed arrow C in FIG. In the period, for example, the following operation (4) is performed instead of the operation (3) described above.

That is, (4) when the receiving area 146c is formed so as to surround the outer peripheral surface of the drive shaft 110 in a wide range in the circumferential direction (encloses the entire circumference in FIG. 9), the rotating body 112 is rotating. , The receiving region 146c is directly opposed to the outlet side opening 147B, and the angular position of the outer peripheral surface side opening end of the first passage 146a is greatly separated from the angular position of the outlet side opening 147B (period). .. Even at this time (period), the lubricating oil received in the receiving area 146c moves radially outward in the receiving area 146c by the centrifugal force associated with the rotation and temporarily stays in the receiving area 146c. However, since the angular position of the outer peripheral surface side opening end of the first passage 146a is largely apart from the angular position of the outlet side opening 147B, the flow of the refrigerant gas flowing out from the outlet side opening 147B is the same as the outer peripheral surface of the first passage 146a. The side open end is not reached or the flow momentum is weakened. As a result, most of the lubricating oil temporarily retained in the receiving area 146c does not flow into the first passage 146a, but flows out of the receiving area 146c by the centrifugal force, and flows through the crank chamber area 140a to the crank chamber. It is stored at the bottom of the chamber 140. Therefore, also in this modification (FIG. 9), the compressor 100 capable of maintaining the proper amount of lubricating oil in the crank chamber 140 while communicating between the crank chamber 140 and the suction chamber 141 is provided. can do.

FIG. 10 is a diagram for explaining a modified example of the oil supply passage 147. In the present embodiment, the outlet-side oil passage 147b of the oil supply passage 147 extends obliquely downward from the one end toward the rotating body 112 side, and then bends toward the axis O of the drive shaft 110 to form the axis O. Although it is assumed that they extend in parallel, the invention is not limited to this. For example, as shown in FIG. 10, the outlet side oil passage 147b may extend obliquely downward as it is toward the rotating body 112 side from the one end to the other end. In this case, for example, the portion on the other end side is expanded in diameter, and the opening of the expanded diameter enlarged portion 147b1 on the rotor 112 side is closed by the end face plate 133a of the thrust bearing 133 except the upper portion. Has been. An upper portion of the opening of the expanded diameter portion 147b1 on the rotor 112 side that is not closed by the end face plate 133a opens to the crank chamber area 140a and constitutes an outlet side opening 147B of the oil supply passage 147. .. As a result, the hole for the outlet side oil passage 147b is machined from one direction on the one end face 102b1 side of the one end wall portion 102b, so that the machining cost of the front housing 102 is reduced.

FIG. 11 is a diagram for explaining a modified example of the thrust bearing 133 shown in FIG. As shown in FIG. 10, when the expanded diameter portion 147b1 is formed at the other end of the outlet side oil passage 147b, a part of the expanded diameter portion 147b1 of the radial inner edge of the end face plate 133a of the thrust bearing 133 is blocked. It is advisable to bend the existing portion 133a1 obliquely toward the receiving area 146c side. The portion 133a1 effectively guides the lubricating oil flowing in the outlet-side oil passage 147b to the receiving area 146c.

FIG. 12 is a diagram for explaining another modification of the oil supply passage 147. In the present embodiment, the outlet-side oil passage 147b extends from the space W toward the crank chamber region 140a, and the space W is provided on the way of the oil supply passage 147, but the present invention is not limited to this. For example, as shown in FIG. 12, the outlet side oil passage 147b may have one end connected in the middle of the inlet side oil passage 147a and the other end extending parallel to the axis O toward the crank chamber area 140a. .. In this case, the outlet-side opening 147B opens in the crank chamber region 140a at a position above the drive shaft 110 in the one end wall portion 102b in the gravity direction and inside the radial inner edge portion of the thrust bearing 133.

FIG. 13 is a diagram for explaining still another modified example of the oil supply passage 147. In the present embodiment, a hole is formed in the one end wall portion 102b of the front housing 102 as the outlet side oil passage 147b, but the present invention is not limited to this. For example, as the first bearing 131, as shown in FIGS. 14 and 15, a shell type needle roller bearing is adopted, and as shown in FIG. 13, the first bearing provided in the crank chamber inner opening portion of the shaft hole 102d. The outlet side oil passage 147b may be configured by a gap between the bearing 131 and the outer peripheral surface of the drive shaft 110. Specifically, the first bearing 131 has a substantially cylindrical outer ring shell 131c and a plurality of needle rollers 131d. One end portion of the outer ring shell 131c is bent inward in the radial direction and is formed as an annular one end surface, and this annular one end surface constitutes one end surface 131a of the first bearing 131. Similarly, the other end of the outer ring shell 131c is bent inward in the radial direction and is formed as a ring-shaped other end surface, and this ring-shaped other end surface constitutes the other end surface 131b of the first bearing 131. The inner diameter D1 of the annular one end surface 131a is set to be larger than the inner diameter D2 of the annular other end surface 131b. Further, the inner diameter D2 of the annular other end surface 131b is slightly larger than the outer diameter of the drive shaft 110, and the gap between the inner edge end of the annular other end surface 131b and the outer peripheral surface of the drive shaft 110 is small. Is set to. Then, the other end surface 131b having an annular shape (that is, the other end portion of the outer ring shell 131c) has a notch 131c1 which has a predetermined width in the circumferential direction and which is notched in a substantially rectangular shape and opens radially inward. It is provided. The first bearing 131 is incorporated in the shaft hole 102d so that the cutout portion 131c1 is on the lower side in the gravity direction. As a result, the cutout portion 131c1 of the first bearing 131 constitutes the outlet side opening 147B of the oil supply passage 147. In this way, the outlet-side oil passage 147b and the outlet-side opening 147B can be formed without making holes in the front housing 102 for the outlet-side oil passage 147b.

FIG. 16 is a diagram for explaining a modified example of the formation mode of the receiving area 146c. In the present embodiment, the receiving area 146c is formed as a recessed area in the one end surface 112b of the rotating body 112, but is not limited to this. For example, as shown in FIG. 16, the receiving portion 148 is provided so as to project from the one end surface 112b of the rotating body 112 toward the one end wall portion 102b, and a part of the outer peripheral surface of the projecting receiving portion 148 and the one end surface 112b. The receiving region 146c may be formed by As described above, the one end surface 112b of the rotating body 112 is, more specifically, the inner wall surface of the annular projecting portion 112c and the outer peripheral surface of the drive shaft 110 among the end surfaces of the rotating body 112 on the one end wall portion 102b side. It is a part between and. In the receiving portion 148, a part of the outer peripheral surface thereof opens to the outer peripheral surface side opening end of the first passage 146a in a part of the angular area in the circumferential direction of the one end surface 112b (area indicated by diagonal lines in FIG. 16). So as to be the facing surface 148a1 and project toward the one end wall portion 102b side. Accordingly, the receiving area 146c can be easily formed on the one end surface 112b of the rotating body 112. In this case, a gap is provided between the projecting end surface of the receiving portion 148 (the end surface on the one end wall portion 102b side) and the one end surface 102b1 of the one end wall portion 102b.

In the present embodiment, the thrust bearing 133 is provided between the rotating body 112 and the one end wall portion 102b of the front housing 102, but the thrust bearing 133 may not be provided at this portion. Further, the first passage 146a opens at an angular position around the axis O corresponding to the link mechanism 120 (see FIG. 3), but the first passage 146a is not limited to this, and an appropriate angle in consideration of the drainage property of the lubricating oil. The position can be opened. The compressor 100 is described as an example of a swash plate type variable displacement compressor with variable discharge capacity, but the compressor 100 is not limited to this, and may be an oscillating plate type variable capacity compressor, or a fixed discharge capacity. It may be a fixed capacity type compressor. Further, as the power source of the rotary power of the drive shaft 110, an appropriate power source such as a motor can be applied.

Although the embodiment of the present invention and the modified example thereof have been described above, the present invention is not limited to the above-described embodiment and the modified example, and further modifications and changes can be made based on the technical idea of the present invention. Is.

Reference numeral 100... Compressor, 101... Cylinder block (housing, crank chamber forming wall, other end wall portion), 101a... Cylinder bore, 102... Front housing (housing, crank chamber forming wall), 102b... One end wall portion, 102b1... One end surface , 102d... Shaft hole, 104... Cylinder head (housing), 110... Drive shaft, 112... Rotating body, 112b... One end face, 131... First bearing (radial bearing), 136... Piston, 140... Crank chamber, 140a... Crank chamber region, 141... Suction chamber, 142... Discharge chamber, 146... Discharge passage, 146a... First passage, 146b... Second passage, 146c... Receiving region, 146c1... Adjacent region, 147... Oil supply passage, 147A... Inlet Side opening, 147B... Exit side opening, 148... Receptor, 148a... Peripheral wall surface, 148a1... Opposing surface, O... Shaft center, R... Rotation direction

Claims

A housing having a suction chamber into which the refrigerant before compression is guided, a discharge chamber, and a crank chamber;
A drive shaft that traverses the crank chamber, the one end portion extending in a shaft hole that is opened in one end wall portion of the crank chamber forming wall of the housing in the drive shaft extending direction,
A radial bearing provided in the shaft hole and rotatably supporting the drive shaft,
A disc-shaped rotating body that is fixed to the drive shaft and faces the one end wall portion in the crank chamber;
A piston housed in a cylinder bore formed in the other end wall portion of the crank chamber forming wall,
A discharge passage that communicates between the crank chamber and the suction chamber,
An oil supply passage for guiding the lubricating oil in the crank chamber to at least the radial bearing;
A compressor, comprising: the refrigerant sucked from the suction chamber into the cylinder bore by the reciprocating motion of the piston in accordance with the rotation of the drive shaft to be discharged to the discharge chamber,
The discharge passage has a first passage extending inward from a predetermined angular position in the circumferential direction on the outer peripheral surface of the one end of the drive shaft, and a first passage extending continuously from the first passage to the other end of the drive shaft. Via the two passages, to communicate between the crank chamber and the suction chamber,
The oil supply passage is provided in the one end wall portion, and an inlet side opening that opens into the crank chamber at a portion of the one end wall portion above the axis of the drive shaft in the direction of gravity is provided. In a crank chamber region between one end face of the one end wall portion and one end face of the rotating body, which is a portion below the inlet side opening in the direction of gravity and at a predetermined angle around the axis of the drive shaft. And an outlet side opening that opens,
Lubricating oil that has flowed into the oil supply passage from the crank chamber through the inlet side opening is configured to flow out from the outlet side opening toward the one end surface of the rotating body,
A receiving portion that forms a receiving region for receiving the lubricating oil that has flowed out from the outlet side opening, and is a radial portion corresponding to the opening position of the outlet side opening on the one end surface of the rotating body. And at least the receiving portion forming the receiving area at a portion including an adjacent area adjacent to the outer peripheral surface side opening end of the first passage,
Including,
The compressor, wherein the outer peripheral surface side opening end of the first passage is open to the adjacent region.
The compressor according to claim 1, wherein the receiving portion has a peripheral wall surface including a facing surface facing the outer peripheral surface side opening end of the first passage.
The compressor according to claim 2, wherein the peripheral wall surface further extends from the facing surface in a rotation direction of the rotating body.
The compressor according to any one of claims 1 to 3, wherein the receiving area is formed so as to partially surround the outer peripheral surface of the drive shaft in a circumferential direction.
The compressor according to claim 4, wherein the adjacent region is located in an end region of the receiving region opposite to a rotation direction of the rotating body.
The compressor according to claim 5, wherein the radial width of the rotating body of the receiving area is formed so as to become narrower toward the end area in the circumferential direction of the rotating body.
The first passage is formed at a plurality of angular positions offset in the circumferential direction on the outer peripheral surface of the drive shaft,
The compressor according to any one of claims 1 to 6, wherein the receiving area is formed corresponding to each of the plurality of first passages.
The compressor according to any one of claims 1 to 7, wherein the receiving area is formed as a recessed area in the one end surface of the rotating body.
The compressor according to any one of claims 1 to 7, wherein the receiving portion is provided so as to project from the one end surface of the rotating body toward the one end wall portion.