JP2007009720A - Variable displacement type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement type compressor capable of making lubricating oil excessively stored in a crankcase flow thereout without controlling pressure in the crankcase. <P>SOLUTION: The compressor is equipped with a suction chamber 39, a compression chamber 43, a discharge chamber 40, a crankcase 16 for accommodating a swash plate 26 rotating with a rotary shaft 20, an air supply passage for communicating between the crankcase 16 and discharge chamber 40, and an extraction passage for communicating between the suction chamber 39 and crankcase 16. The extraction passage consists of a first passage for communicating with the crankcase 16, a second passage which communicates with the crankcase through a different route from the first passage and which is formed on the outer peripheral side from the first passage in a radial direction of the rotary shaft 20, a merging part in which the first passage and second passage merge with each other, and an opening/closing means which includes a restrictor formed between the merging part and suction chamber 39 to open/close at least one of the first and second passages. The second passage is opened when the temperature in the crankcase 16 is a prescribed temperature or higher. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a variable displacement compressor, and more particularly, to a variable displacement compressor including a passage through which excessively stored lubricating oil is passed outside the crank chamber.

Generally, a variable capacity compressor (hereinafter simply referred to as “compressor”) capable of variably controlling a discharge capacity is known as a compressor used in a vehicle air conditioner or the like.
This type of compressor has a cylinder block in which a cylinder bore is formed, a front housing joined to the front end of the cylinder block, and a rear housing in which a suction chamber and a discharge chamber are formed.
A crank chamber is formed inside the front housing, and a rotary shaft is rotatably supported on the front housing. The rotary shaft is connected to be rotated by an external drive source such as an engine.
A swash plate that can tilt with respect to the rotation shaft is housed in the crank chamber. The swash plate rotates in synchronization with the rotation shaft, and the piston housed in the cylinder bore reciprocates with a piston stroke corresponding to the tilt state of the swash plate. Move.

The piston stroke is determined by the pressure difference between the pressure in the crank chamber and the suction pressure, but the swash plate approaches a right angle to the axis of the rotating shaft as the crank chamber pressure increases (the inclination angle of the swash plate decreases). In addition, when the pressure in the crank chamber is low, the swash plate is inclined so as to approach the axis of the rotating shaft (the inclination angle of the swash plate increases).
That is, when the crank chamber pressure is high and the swash plate tilt angle is small, the piston stroke is small. Conversely, when the crank chamber pressure is low and the swash plate tilt angle is large, the piston stroke is large. .
Therefore, the discharge capacity decreases as the piston stroke decreases, and the discharge capacity increases as the stroke increases.

In this type of compressor, in order to change the discharge capacity, a part of the high-pressure refrigerant is supplied from the discharge chamber to the crank chamber, and during the compression stroke, the high-pressure refrigerant is discharged from the compression chamber through a minute gap between the cylinder bore and the piston. Part of the refrigerant (hereinafter referred to as “blow-by gas”) and lubricating oil flow into the crank chamber.
The lubricating oil flowing into the crank chamber is scattered in the form of a mist toward the outer peripheral side in the radial direction of the rotating shaft by the centrifugal force of the rotating shaft.
Therefore, the density of the lubricating oil is low in the vicinity of the axis of the rotating shaft in the crank chamber, and the density of the lubricating oil increases as it approaches the crank chamber wall.
For this reason, by providing a bleed passage for connecting the crank chamber and the suction chamber at a position close to the rotation shaft or in the rotation shaft, the outflow of the lubricating oil from the crank chamber to the suction chamber is suppressed, so that the lubricating oil flows into the crank chamber. Will be stored.

If the lubricating oil adheres to the heat exchanger inner wall of the external refrigerant circuit during the operation of the compressor, the heat exchange rate decreases.
In order to prevent this decrease in heat exchange efficiency and to lubricate each sliding portion inside the compressor, it is desirable to store the lubricating oil in the compressor as much as possible.
However, if the lubricating oil accumulates excessively in the crank chamber, the rotating swash plate stirs the lubricating oil stored in the crank chamber, but the stirring resistance caused by this stirring may increase the temperature of the compressor.
The high temperature of the compressor is a factor that causes a decrease in the reliability of the compressor, for example, by promoting the deterioration of the lip seal that prevents refrigerant leakage along the peripheral surface of the rotating shaft.

Therefore, conventionally, for example, a compressor provided with an open / close passage as disclosed in JP-A-2001-123946 has been proposed.
In this compressor, an extraction passage that communicates the crank chamber and the suction chamber is provided.
One extraction passage always communicates with the crank chamber and the suction chamber, and a bimetal is disposed in the other extraction passage.
According to this compressor, when the swash plate agitates the lubricating oil stored excessively in the crank chamber, the compressor heats up, but when the temperature in the crank chamber increases, the bimetal is bent and deformed, so that the bleed passage To lower the pressure in the crank chamber, increase the inclination angle of the swash plate, and increase the discharge capacity.
The increase in the discharge capacity promotes the outflow of lubricating oil that is excessively stored in the crank chamber, thereby suppressing the high temperature of the compressor.
JP 2001-123946 A

However, the compressor disclosed in Patent Document 1 can extract the lubricating oil excessively stored in the crank chamber through the extraction passage, but if the pressure in the crank chamber is not lowered by opening the extraction passage by bimetal, There is a problem that excessive lubricating oil cannot be sufficiently discharged from the extraction passage.
In other words, this is merely a technique that intends to flow out excess lubricating oil stored in the crank chamber based on pressure control in the crank chamber.
Incidentally, lowering the pressure in the crank chamber for the purpose of causing excess lubricating oil to flow out increases the capacity unrelated to temperature control, and causes, for example, excessive power loss and inconsistency with control.

  The present invention has been made in view of the above-mentioned problems, and an object of the present invention is to allow lubricant oil excessively stored in the crank chamber to flow out of the crank chamber while suppressing pressure fluctuations in the crank chamber. To provide a variable capacity compressor.

  In order to achieve the above object, the invention according to claim 1 includes a suction chamber for sucking low-pressure refrigerant from the outside, a compression chamber for compressing the refrigerant, a discharge chamber for discharging the compressed high-pressure refrigerant, A crank chamber that houses a swash plate that rotates together with the rotating shaft; an air supply passage that connects the crank chamber and the discharge chamber; and a bleed passage that connects the suction chamber and the crank chamber. In the variable displacement compressor that varies the discharge capacity based on the fluctuation, the extraction passage communicates with the crank chamber through a first passage communicating with the crank chamber, a path different from the first passage, and the A second passage formed on the outer peripheral side of the first passage in the radial direction of the rotation shaft, a joining portion where the first passage and the second passage join each other, and between the joining portion and the suction chamber Including the aperture formed Comprises a closing means for opening and closing at least one of said first passage and said second passage, said second passage, characterized in that the temperature of the crank chamber is open at a predetermined temperature or higher.

According to the first aspect of the present invention, when the swash plate rotates at a high speed in a state where the lubricating oil is excessively stored in the crank chamber, the temperature of the crank chamber becomes high, but the temperature of the crank chamber exceeds a predetermined temperature. When reaching, the second passage in the bleed passage is at least open.
The second passage is formed on the outer peripheral side in the radial direction of the rotation shaft with respect to the first passage. As described above, the closer to the outer peripheral side, the higher the density of the lubricating oil. Therefore, the amount of lubricating oil discharged from the crank chamber to the suction chamber is larger in the second passage than in the first passage.
For this reason, if the temperature of the crank chamber is equal to or higher than the predetermined temperature and the second passage is opened, the amount of lubricating oil stored in the crank chamber decreases, and even if the swash plate rotates at high speed, it is stored in the swash plate and the crank chamber. The agitation resistance with the lubricating oil is suppressed as the amount of lubricating oil stored decreases.
In addition, since the circulation amount of the refrigerant gas flowing out from the crank chamber to the suction chamber is always set by the restriction in the extraction passage regardless of whether the second passage is open or closed, the opening and closing of the second passage opens the crank chamber. The pressure of the will not fluctuate.
That is, without changing the capacity of the compressor, it is possible to reduce the lubricating oil excessively stored in the crank chamber, suppress the temperature increase in the crank chamber, and suppress the decrease in the reliability of the compressor.
The diaphragm may be a fixed diaphragm having a constant diaphragm opening, or a variable diaphragm capable of adjusting the diaphragm opening.

  According to a second aspect of the present invention, in the variable capacity compressor according to the first aspect, the opening / closing means has a first passage opening / closing mechanism for opening / closing the first passage, and a temperature in the crank chamber is equal to or higher than a predetermined temperature. In this case, the first passage opening / closing mechanism closes the first passage.

According to the second aspect of the present invention, when the temperature in the crank chamber is equal to or higher than the predetermined temperature, the first passage opening / closing mechanism closes the first passage.
When the temperature in the crank chamber is equal to or higher than the predetermined temperature, the first passage opening / closing mechanism closes the first passage, so that the lubricating oil in the crank chamber flows out only through the second passage in the opened state. Therefore, the amount of lubricating oil discharged from the crank chamber to the suction chamber can be increased as compared with the case where the first passage is open.

  According to a third aspect of the present invention, in the variable capacity compressor according to the first aspect, the opening / closing means has a second passage opening / closing mechanism for opening / closing the second passage, and a temperature in the crank chamber is equal to or higher than a predetermined temperature. In this case, the second passage opening / closing mechanism opens the second passage.

According to the invention of claim 3, when the temperature in the crank chamber is equal to or higher than a predetermined temperature, the second passage opening / closing mechanism opens the second passage.
When the temperature in the crank chamber is equal to or higher than the predetermined temperature, the second passage opening / closing mechanism opens the second passage, so that the lubricating oil in the crank chamber flows out through the opened second passage.

  According to a fourth aspect of the present invention, in the variable displacement compressor according to the first aspect, the opening / closing means includes a first passage opening / closing mechanism for opening / closing the first passage and a second passage opening / closing for opening / closing the second passage. The first passage opening / closing mechanism opens the first passage, and the second passage opening / closing mechanism closes the second passage when the temperature of the crank chamber is lower than a predetermined temperature. When the temperature is equal to or higher than a predetermined temperature, the first passage opening / closing mechanism closes the first passage, and the second passage opening / closing mechanism opens the second passage.

According to the invention of claim 4, when the temperature of the crank chamber is lower than the predetermined temperature, the first passage opening / closing mechanism opens the first passage, and the second passage opening / closing mechanism closes the second passage.
On the other hand, when the temperature of the crank chamber is equal to or higher than a predetermined temperature, the first passage opening / closing mechanism closes the first passage and the second passage opening / closing mechanism opens the second passage.
For this reason, when the temperature of the crank chamber is lower than the predetermined temperature, the lubricating oil in the crank chamber flows out only to the first passage through the first passage.
For example, when the density of the lubricating oil near the inlet of the first passage is lower than the density of the lubricating oil near the inlet of the second passage, the flow rate of the lubricating oil passing through the first passage passes through the second passage. Less than when.
In other words, when the temperature of the crank chamber is lower than the predetermined temperature and there is no risk of the compressor becoming hot due to the stirring of the lubricating oil, it is necessary to suppress the outflow of the lubricating oil from the crank chamber to the suction chamber. Sufficient lubricating oil can be stored.
On the other hand, when the temperature of the crank chamber is equal to or higher than the predetermined temperature, the lubricating oil in the crank chamber flows out only to the second passage through the second passage.
For example, when the density of the lubricating oil near the entrance of the second passage is higher than the density of the lubricating oil near the entrance of the first passage, the flow rate of the lubricating oil through the second passage is such that the lubricating oil passes through the first passage. More than when.
In other words, when the temperature of the crank chamber is equal to or higher than the predetermined temperature and there is a risk of causing the compressor to become hot due to agitation of the lubricating oil, the crank chamber can be moved from the crank chamber to the suction chamber without excessive storage of the lubricating oil. Lubricating oil can be sufficiently discharged.

  The invention according to claim 5 is the variable capacity compressor according to any one of claims 1 to 4, wherein the second passage has an opening facing the crank chamber, and the opening is the crank chamber. It is arrange | positioned near the surrounding wall of this.

According to the fifth aspect of the present invention, the lubricating oil in the crank chamber is easily biased to the peripheral wall of the crank chamber due to the centrifugal force due to the rotation of the rotating elements such as the swash plate and the rotating shaft, but the second passage of the crank chamber faces the crank chamber. Since the opening is disposed closer to the peripheral wall of the crank chamber, more lubricating oil is passed through the second passage when the second passage is opened.
Therefore, when the second passage is opened, excess lubricating oil can be quickly and efficiently discharged from the second passage.

  A sixth aspect of the present invention is the variable capacity compressor according to any one of the first to fifth aspects, wherein the opening / closing means includes an opening / closing member formed of a bimetal or a shape memory alloy. .

According to the sixth aspect of the present invention, when the temperature of the crank chamber reaches a predetermined temperature or higher due to stirring of the lubricating oil excessively stored in the crank chamber and the swash plate that rotates at a high speed, it is formed of bimetal or shape memory alloy. The opening / closing member that closes, for example, closes the first passage or opens the second passage.
Since the opening / closing member is formed of a bimetal or a shape memory alloy, the opening / closing of the first passage and the second passage according to the temperature can be realized by providing the opening / closing member.

  A seventh aspect of the present invention provides the variable capacity compressor according to any one of the first to sixth aspects, wherein the opening / closing means includes a temperature detector for detecting a temperature in the crank chamber, and a temperature detector. An opening / closing tool for opening and closing the corresponding passage based on the detection output is included.

According to the seventh aspect of the present invention, when the temperature of the crank chamber reaches a predetermined temperature or higher due to stirring of the lubricating oil excessively stored in the crank chamber and the swash plate rotating at a high speed, the temperature detecting body is at a high temperature. The opening / closing tool opens and closes the corresponding passage based on the output of the temperature detection body.
By providing the temperature detecting body and the opening / closing tool independently, it is possible to freely set a predetermined temperature to be detected or to open / close reliably from the corresponding passage.

  The invention according to claim 8 is the variable displacement compressor according to any one of claims 1 to 7, wherein the first passage is an in-shaft passage formed inside the rotary shaft. It is characterized by including.

  According to the eighth aspect of the present invention, the first passage includes the in-shaft passage formed inside the rotating shaft, thereby suppressing the amount of lubricating oil flowing out from the crank chamber to the suction chamber via the first passage. This makes it easier to store the lubricating oil.

  According to the present invention, it is possible to provide a variable capacity compressor capable of causing the lubricating oil excessively stored in the crank chamber to flow out of the crank chamber while suppressing pressure fluctuations in the crank chamber.

(First embodiment)
The variable capacity compressor (hereinafter simply referred to as “compressor”) according to the first embodiment will be described below with reference to FIGS. 1 and 2.
The compressor 10 shown in FIG. 1 includes a housing 11 that is an outer shell of the compressor 10. The housing 11 includes a cylinder block 12 having a plurality of cylinder bores 12 a and a cylinder block 12. The front housing 13 is joined to the front side, and the rear housing 14 is joined to the rear side of the cylinder block 12.
The front housing 13, the cylinder block 12, and the rear housing 14 are integrally fixed by fastening the through bolts 15 passed from the front housing 13 to the rear housing 14 in the front-rear direction, and the housing 11 is formed.

A crank chamber 16 is formed in the front housing 13 with the rear side closed by the cylinder block 12.
The peripheral wall of the crank chamber 16 is mainly formed by the peripheral wall 12 b of the cylinder block 12 and the peripheral wall 13 b of the front housing 13.
A through hole penetrating forward from the crank chamber 16 is formed in the front housing 13.
A rotatable rotating shaft 20 is provided so as to pass through the vicinity of the center of the crank chamber 16. The rotating shaft 20 includes a radial bearing 21 provided in the through hole and another radial provided in the cylinder block 12. It is supported by a bearing 22.
That is, the rotating shaft 20 in the front housing 13 and the cylinder block 12 is supported by the radial bearing 21 at the front and horizontally by the radial bearing 22 at the rear.

The front housing 13 is formed with a shaft seal member accommodating portion 18 in front of the radial bearing 21, and the shaft seal member accommodating portion 18 is provided with a shaft seal member 23 that is in sliding contact with the circumferential surface of the rotary shaft 20. Yes.
The shaft seal member 23 of this embodiment is a lip seal and prevents the refrigerant in the crank chamber 16 from leaking from between the front housing 13 and the rotary shaft 20.
Further, the front housing 13 is formed with a conduction path 13a that communicates from the vicinity of the thrust bearing 19 to the shaft sealing member accommodating portion 18, and supplies the lubricating oil in the crank chamber 16 to the shaft sealing member 23 through the conduction path 13a. It has become something that can be.

In this embodiment, the front end of the rotating shaft 20 is connected to an external drive source via a power transmission mechanism (not shown), and is a clutchless mechanism by a combination of a belt and a pulley that can always transmit power. .
The power transmission mechanism is not limited to the clutchless mechanism, and the power transmission mechanism may employ a clutch mechanism such as an electromagnetic clutch that can select transmission or interruption of power by external electric control.

A lug plate 24 is fixed to the rotary shaft 20 in the crank chamber 16 so as to be integrally rotatable.
A swash plate 26 constituting a part of the capacity changing mechanism 25 is supported on the rotary shaft 20 behind the lug plate 24 so as to be slidable and tiltable in the axial direction of the rotary shaft 20.
A hinge mechanism 27 is interposed between the swash plate 26 and the lug plate 24, and the swash plate 26 is connected to the lug plate 24 and the rotary shaft 20 through the hinge mechanism 27 so as to be capable of synchronous rotation and tilting. ing.
The capacity changing mechanism 25 of this embodiment includes a lug plate 24 and a hinge mechanism 27 in addition to the swash plate 26.
A thrust bearing 19 is interposed between the outer peripheral front surface of the lug plate 24 and the inner surface of the front housing 13, and the thrust housing force generated in the lug plate 24 can be received by the front housing 13 via the thrust bearing 19. It has become.

A coil spring 28 is wound between the lug plate 24 and the swash plate 26 in the rotary shaft 20, and a slidable cylindrical body 29 urged rearward by the pressing of the coil spring 28 is a rotary shaft. 20 is inserted.
The swash plate 26 is always pressed backward, that is, in a direction in which the inclination angle of the swash plate 26 decreases, by the cylindrical body 29 that receives the urging force of the coil spring 28.
Here, the inclination angle of the swash plate 26 means an angle formed by a surface orthogonal to the rotation axis 20 and a surface of the swash plate 26.

A stopper portion 26a projects from the front portion of the swash plate 26. As shown in FIG. 1, the stopper portion 26a abuts on the lug plate 24 so that the maximum inclination position of the swash plate 26 is regulated. It has become.
A retaining ring 30 is attached to the rotating shaft 20 behind the swash plate 26, and another coil spring 31 is wound around the rotating shaft 20 in front of the retaining ring 30.
By contacting the front portion of the coil spring 31, the minimum inclination position of the swash plate 26 is regulated as shown by a two-dot chain line in FIG.
Further, another coil spring 32 is interposed between the rear end of the rotating shaft 20 and the rear housing 14, and always urges the rotating shaft 20 forward.
Further, a spring accommodating portion 17 that accommodates the coil spring 32 is formed across the cylinder block 12 and the rear housing 14.

In each cylinder bore 12 a of the cylinder block 12, a single-headed piston 33 is accommodated so as to be able to reciprocate, and the neck portion of these pistons 33 is anchored to the outer periphery of the swash plate 26 via a shoe 34.
Then, when the swash plate 26 is rotationally moved with the rotation of the rotary shaft 20, each piston 33 is reciprocated through the shoe 34.

On the other hand, as shown in FIG. 1, the front side of the rear housing 14 and the rear side of the cylinder block 12 are joined, but a valve plate 35 and a valve body forming plate 36 are interposed between the two 14 and 12. 37 and a retainer 38 are interposed.
The rear housing 14 is a rear housing joined to the cylinder block 12. A suction chamber 39 is formed at the center of the rear housing 14, and the suction chamber 39 is provided in the valve plate 35. The suction port 41 communicates with the compression chamber 43 in the cylinder bore 12a.
Further, a discharge chamber 40 is formed on the outer peripheral side of the rear housing 14, and the discharge chamber 40 and the suction chamber 39 are separated by a partition wall 14a.

The valve plate 35 is for forming the compression chamber 43 together with the piston 33 in the cylinder bore 12a, and has a suction port 41 communicating with the suction chamber 39 on the rear housing 14 side and a discharge port 42 communicating with the discharge chamber 40. is doing.
The valve body forming plate 36 is a suction valve forming plate that forms a suction valve (not shown) interposed between the compression chamber 43 and the suction port 41, while the valve body forming plate 37 is a discharge port 42. And a discharge valve forming plate for forming a lead type discharge valve 37 a interposed between the discharge chamber 40 and the discharge chamber 40.
The retainer 38 is for restricting the maximum opening of the discharge valve 37a.

By the way, the refrigerant in the suction chamber 39 is sucked into the compression chamber 43 through the suction port 41 and the suction valve by the movement from the top dead center position to the bottom dead center position of the piston 33.
The refrigerant sucked into the compression chamber 43 is compressed to a predetermined pressure by moving from the bottom dead center position of the piston 33 to the top dead center position, and is discharged to the discharge chamber 40 through the discharge port 42 and the discharge valve 37a. The
The inclination angle of the swash plate 26 is determined based on a mutual balance with each moment such as a moment of rotational motion caused by the centrifugal force of the swash plate 26, a moment caused by the reciprocating inertia force of the piston 33, and a moment caused by the refrigerant pressure.
The moment due to the pressure of the refrigerant is a moment generated based on the correlation between the pressure in the compression chamber 43 and the pressure in the crank chamber 16 acting on the back surface of the piston 33 and is inclined according to the pressure fluctuation in the crank chamber 16. It acts in the direction of increasing or decreasing the angle.

In the compressor 10 of this embodiment, the inclination angle of the swash plate 26 is adjusted by adjusting the pressure in the crank chamber 16 using the capacity control valve 44 provided in the rear housing 14 and appropriately changing the moment due to the pressure of the refrigerant. Can be set to an arbitrary angle between the minimum inclination angle and the maximum inclination angle.
The capacity control valve 44 of this embodiment is a control valve that performs supply control for supplying a part of the refrigerant having the discharge pressure to the crank chamber 16.
Although not shown, the refrigerant supply passage for the discharge pressure is mainly composed of a control passage communicating the discharge chamber 40 and the capacity control valve 44 and a control passage communicating the capacity control valve 44 and the crank chamber 16.

On the other hand, a passage for extracting the refrigerant in the crank chamber 16 to the suction chamber 39, that is, an extraction passage is provided.
The extraction passage of this embodiment mainly includes a first passage, a second passage having a different route from the first passage, and joining the first passage, a joining portion of the first passage and the second passage, a joining portion, A throttle formed between the suction chamber 39 and the suction chamber 39 is included.
Specifically, as shown in FIG. 1, the first passage is an in-shaft passage 45 provided mainly in the rotary shaft 20 and communicating with the crank chamber 16.
The second passage is a lubricating oil passage 48 provided in the cylinder block 12 separately from the first passage.
The spring accommodating portion 17 in which the spring 32 is accommodated is a joining portion of the in-shaft passage 45 serving as the first passage and the lubricating oil passage 48 serving as the second passage.
The throttle is a fixed throttle 46 that communicates the spring accommodating portion 17 and the suction chamber 39.
The front end of the in-shaft passage 45 communicates with the shaft seal member accommodating portion 18, and the rear end communicates with the spring accommodating portion 17.
An intermediate branch passage 47 communicating with the vicinity of the swash plate 26 of the crank chamber 16 is formed in the middle of the in-shaft passage 45.
The intermediate branch passage 47 is provided at a position where the intermediate branch passage 47 is blocked by the tubular member 29 that moves rearward when the inclination angle of the swash plate decreases.

On the other hand, the shaft seal member accommodating portion 18 communicates with the crank chamber 16 through a conduction path 13 a formed from the vicinity of the outer periphery of the lug plate 24 and toward the rotary shaft 20.
Accordingly, the lubricating oil can be supplied from the crank chamber 16 to the shaft sealing member 23 and further passed through the in-shaft passage 45.
The fixed throttle 46 has a narrow passage area, and the fixed throttle 46 can set the refrigerant gas circulation amount from the crank chamber 16 to the suction chamber 39.

Next, referring to the second passage, the second passage in this embodiment is a lubricating oil passage 48 that has an opening 49 a in the peripheral wall 12 b of the cylinder block 12 and merges with the spring accommodating portion 17.
The lubricating oil passage 48 includes an opening-side passage 49 that is parallel to the axis of the rotary shaft 20, and a merging-side passage 50 that leads from the opening-side passage 49 to the spring accommodating portion 17.
As shown in FIG. 2, the opening 49a side of the opening-side passage 49 is a small-diameter passage 49b, and the merging-side passage 50 side is a large-diameter passage 49c compared to the opening 49a side.
A step is formed at the boundary between the small-diameter and large-diameter passages in the opening-side passage 49.
A connecting portion between the opening-side passage 49 and the merging-side passage 50 is provided with a second passage opening / closing mechanism 51 as an opening / closing means for opening / closing the lubricating oil passage 48.
As shown in FIG. 2A, the second passage opening / closing mechanism 51 of this embodiment is a bimetallic coil spring 52 that extends at a predetermined temperature (hereinafter referred to as “bimetallic spring 52” for convenience). And a cylindrical valve body 53 that opens and closes the lubricating oil passage 48 by the bimetal spring 52, and a coil spring 55 that urges the cylindrical valve body 53 in a direction to close the lubricating oil passage 48.
The bimetal spring 52 corresponds to the opening / closing member of the second passage opening / closing mechanism 51.

The bimetal spring 52 is housed in a passage 49 c on the large diameter confluence side passage 50 side in the opening side passage 49.
The bimetal spring 52 of this embodiment is in a state where it does not expand at a low temperature below a predetermined temperature (for example, about 150 ° C.), for example, and expands at a high temperature above the predetermined temperature and becomes longer than at a low temperature. It is intended to do.
Specifically, as shown in FIG. 2B, the bimetal spring 52 is a combination of materials 52 a and 52 b having different expansion rates, and one material 52 a is a spring at each part of the bimetal spring 52. One of the lengths always faces and the other material 52b always faces the rear side.

The cylindrical valve body 53 is a cylindrical valve body having a through hole 53a, and is accommodated in a valve body accommodating portion 54 formed rearward from the opening-side passage 49.
The valve body accommodating portion 54 is set to have a diameter larger than that of the passage 49 c, and the upstream end of the merging side passage 50 is connected to the front portion of the valve body accommodating portion 54.
Since the outer diameter of the tubular valve body 53 corresponds to the valve pair housing portion 54, the tubular valve body 53 can move back and forth in the valve body housing portion 54.
The valve body accommodating portion 54 accommodates a coil spring 55 that urges the cylindrical valve body 53 from the rear to the front.
The coil spring 55 is a general coil spring, and biases the cylindrical valve body 53 in the direction in which the lubricating oil passage 48 is closed.
Therefore, the cylindrical valve body 53 is in a state of being interposed between the bimetal spring 52 and the coil spring 55.
The cylindrical valve body 53 closes the lubricating oil passage 48 when the temperature is low, and the cylindrical valve body 53 resists the biasing force of the coil spring 55 due to the biasing force based on the extension of the bimetal spring 52 when the temperature is high. As a result, the cylindrical valve body 53 moves rearward and opens the lubricating oil passage 48.
Therefore, the urging force based on the extension of the bimetal spring 52 needs to be set larger than the urging force of the coil spring 55.

Next, the outflow of lubricating oil excessively stored in the crank chamber 16 by the compressor 10 according to this embodiment will be described.
When the swash plate 26 rotates with the rotation of the rotary shaft 20, each piston 33 is reciprocated through the shoe 34.
Thereby, when each piston 33 is moved from the top dead center position to the bottom dead center position, the refrigerant in the suction chamber 39 is sucked into the compression chamber 43 in the cylinder bore 12a through the suction port 41.
Thereafter, when each piston 33 is moved from the bottom dead center position to the top dead center position, the refrigerant in the compression chamber is compressed to a predetermined pressure.
At this time, the refrigerant in a high pressure state pushes up the discharge valve 37a from the compression chamber 43 and is discharged into the discharge chamber 40, and then the refrigerant is discharged into a discharge pipe connected to an external refrigerant circuit or the like.

For example, when the vehicle interior temperature is high, the supply of the refrigerant at the discharge pressure into the crank chamber 16 is reduced by the control of the capacity control valve 44, while the refrigerant in the crank chamber 16 leads the extraction passage to the suction chamber 39. The compressor 10 quickly increases the inclination angle of the swash plate 26 to increase the discharge capacity.
When the discharge capacity increases, lubricating oil flows into the crank chamber 16 together with blow-by gas.
A part of the lubricating oil that flows in flows into the suction chamber 36 from the shaft passage 45, but most of the lubricating oil drops or mists near the peripheral wall 12 b of the crank chamber 16 due to the centrifugal force accompanying the rotation of the rotating shaft 20. And is stored in the crank chamber 16.

Part of the lubricating oil that has flowed into the crank chamber 16 is supplied to the shaft seal member 23 through the conduction path 13a.
Further, a part of the lubricating oil supplied to the shaft seal member 23 and the lubricating oil entering the in-shaft passage 45 from the intermediate branch passage 47 pass through the spring accommodating portion 17 from the in-shaft passage 45 and lubricate the radial bearing 22. At the same time, it is led out to the suction chamber 39 through the fixed throttle 46.

  When the lubricating oil is stored in the crank chamber 16, when the swash plate 26 rotates at low speed, the lubricating oil is sufficiently supplied to the sliding members such as the swash plate 26 and the shaft seal member 23, thereby suppressing sliding heat generation. can do. However, when the swash plate 26 rotates at a high speed (for example, when the rotational speed exceeds 4000 to 5000 rpm), the heat generated by the shear friction due to the stirring of the lubricating oil and the swash plate 26 exceeds the sliding heat generated by the sliding member. Therefore, the temperature in the crank chamber 16 rises.

In this embodiment, when the temperature in the crank chamber 16 is lower than a predetermined temperature (for example, about 150 ° C.), the second passage opening / closing mechanism 51 closes the lubricating oil passage 48, specifically, a cylindrical shape When the valve body 53 closes the upstream end of the merging side passage 50, the lubricating oil passage 48 is in a state of being interrupted on the way.
When the temperature in the crank chamber 16 rises to exceed a predetermined temperature (for example, about 150 ° C.), the second passage opening / closing mechanism 51 opens the lubricating oil passage 48.
Specifically, when the temperature in the crank chamber 16 exceeds a predetermined temperature, the bimetal spring 52 is extended, and the urging force based on the extension of the bimetal spring 52 causes the cylindrical valve body 53 to urge the coil spring 55. It moves to the rear against this and opens the opening side passage 49 in the lubricating oil passage 48.
When the opening side passage 49 is opened, the opening side passage 49 and the merging side passage 50 communicate with each other, and the lubricating oil excessively stored in the crank chamber 16 can be passed to the lubricating oil passage 48.
The excessively stored lubricating oil in the crank chamber 16 is caused by the differential pressure between the crank chamber 16 and the suction chamber 39 and the centrifugal force due to the rotation of the rotating elements in the crank chamber 16 including the swash plate 26 and the rotating shaft 20. The oil passes through the lubricating oil passage 48 and flows out from the spring accommodating portion 17 to the suction chamber 39 through the fixed throttle 46.

Due to the outflow of excess lubricating oil from the crank chamber 16 through the lubricating oil passage 48, the lubricating oil in the crank chamber 16 is reduced, and the shear friction due to the agitation between the lubricating oil and the swash plate 26 is reduced.
By reducing the shear friction between the lubricating oil and the swash plate 26, heat generation due to the shear friction is suppressed, and the temperature rise in the crank chamber 16 is suppressed.
When the temperature rise is suppressed and the temperature in the crank chamber 16 falls below a predetermined temperature, the bimetal spring 52 is shortened and the cylindrical valve body 53 closes the opening side passage 49 in the lubricating oil passage 48.
When the lubricating oil passage 48 is closed by the second passage opening / closing mechanism 51, at least the lubricating oil required by the sliding portion in the crank chamber 16 remains in the crank chamber 16.

Thus, for example, when the compressor having excessively stored lubricating oil in the crank chamber 16 rotates at a high speed, the excessive lubricating oil is discharged from the crank chamber 16 through the lubricating oil passage 48 and the swash plate 26. Heat generation due to shear friction with excess lubricating oil is suppressed.
On the other hand, in the compressor 10 in which the lubricating oil is excessively stored in the crank chamber 16, when the swash plate 26 rotates at a low speed, the lubricating oil is sufficiently retained in the crank chamber 16, and the sliding portion in the crank chamber 16 is retained. Is ensured without a shortage of necessary lubricating oil.

The compressor 1 according to this embodiment has the following effects.
(1) If the swash plate 26 rotates at a high speed while the lubricating oil is excessively stored in the crank chamber 16, the temperature in the crank chamber 16 becomes high, but the temperature in the crank chamber 16 reaches a predetermined temperature or higher. At this time, the lubricating oil passage 48 in the extraction passage is opened by the second passage opening / closing mechanism 51. When the lubricating oil passage 48 is opened, excess lubricating oil flows out to the suction chamber 39 through the lubricating oil passage 48 and the fixed throttle 46. For this reason, the amount of lubricating oil stored in the crank chamber 16 decreases, and even if the swash plate 26 rotates at high speed, the stirring resistance between the swash plate 26 and the lubricating oil stored in the crank chamber 16 causes the lubricating oil to be stored. Suppressed as the amount decreases. Further, regardless of whether the lubricating oil passage 48 is open or closed, the amount of refrigerant gas circulating from the crank chamber 16 to the suction chamber 39 is always set by the fixed throttle 46 in the extraction passage. The pressure in the crank chamber 16 does not fluctuate due to opening and closing. That is, without changing the capacity of the compressor 10, the lubricating oil in which the lubricating oil is excessively stored in the crank chamber 16 is reduced, and the rise in the temperature in the crank chamber 16 is suppressed, thereby improving the reliability of the compressor 10. The decrease can be suppressed.

(2) The lubricating oil in the crank chamber 16 is easily biased to the peripheral walls 12b and 13b of the crank chamber 16 due to the centrifugal force due to the rotation of the rotating elements such as the swash plate 26 and the rotating shaft 20, but the lubricating oil facing the crank chamber 16 Since the opening 49a of the passage 48 is disposed closer to the peripheral walls 12b and 13b of the crank chamber 16, more lubricating oil is passed through the lubricating oil passage 48 when the lubricating oil passage 48 is opened. Therefore, when the lubricating oil passage 48 is opened, excess lubricating oil can be quickly and efficiently discharged from the lubricating oil passage 48.
(3) When the temperature of the crank chamber 16 reaches a predetermined temperature or more due to stirring of the lubricating oil excessively stored in the crank chamber 16 and the swash plate 26 that rotates at a high speed, the cylindrical valve body 53 extends the bimetal spring 52. Thus, the lubricating oil passage 48 is opened. Since the bimetal spring 52 is formed by a combination of materials 52a and 52b having different expansion rates, the cylindrical valve body 53, the bimetal spring 52, and the coil spring 55 are provided, so that the lubricating oil passage 48 corresponding to the temperature is provided. Opening and closing can be realized.
(4) The first passage includes the in-shaft passage 45 formed inside the rotary shaft 20, so that it is easy to supply the lubricant to the elements around the rotary shaft 20. By connecting the shaft seal member accommodating portion 18 in which the shaft seal member 23 is accommodated and the crank chamber 16 to each other and the passage communicating with the shaft seal member accommodating portion 18 is included in the shaft passage 45, Lubrication of the shaft seal member 23 with the lubricating oil in the chamber 16 is facilitated. Further, since the density of the lubricating oil is low near the rotary shaft 20 and the amount of lubricating oil flowing out to the suction chamber 39 through the first passage is small, the lubricating oil can be efficiently stored in the crank chamber 16.

(Second Embodiment)
Next, the compressor 60 according to the second embodiment will be described with reference to FIG.
Since most of the compressor 60 of this embodiment is the same as that of the first embodiment, the same reference numerals are used for elements that are the same as or similar to those of the first embodiment, and the description of the first embodiment is given. Incorporate.
In the compressor 60 of this embodiment, as shown to Fig.3 (a), the 1st channel | path mainly formed in the rotating shaft 20 and the 2nd channel | path formed in the cylinder block 12 and merged with a 1st channel | path are comprised. I have.
The first passage is an in-shaft passage 62 mainly provided in the rotary shaft 20.
The spring accommodating portion 17 in which the spring 32 is accommodated is a joining portion between the in-shaft passage 62 as the first passage and the second passage.
The throttle is a fixed throttle 46 that communicates the spring accommodating portion 17 and the suction chamber 39.
An intermediate branch path 63 communicating with the vicinity of the swash plate 26 of the crank chamber 16 is formed in the middle of the in-shaft passage 62.
In this embodiment, the in-shaft passage 62 includes a small-diameter passage 62 a and a large-diameter passage 62 b, and the front end of the in-shaft passage 62 is not communicated with the shaft seal member housing portion 18, and The end communicates with the spring accommodating portion 17.
Accordingly, the in-shaft passage 62 as the first passage is a passage limited to the communication between the crank chamber 16 and the suction chamber 39.
The first passage of this embodiment is provided with a first passage opening / closing mechanism 61 as opening / closing means for opening / closing the first passage.
The first passage opening / closing mechanism 61 corresponds to an opening / closing means. As shown in FIGS. 3A and 3B, a bimetallic coil spring 64 that extends at a predetermined temperature as a boundary (hereinafter referred to as “bimetallic spring” for convenience). 64 ”), and a cylindrical valve body 65 that opens and closes the first passage by the bimetal spring 64, and a coil spring 66 that biases the cylindrical valve body 65.
The bimetal spring 64 corresponds to the opening / closing member of the first passage opening / closing mechanism 61.

The bimetal spring 64 is accommodated in a large-diameter passage 62b in the in-shaft passage 62, and urges the tubular valve body 65 in a direction to close the intermediate branch passage 63.
On the other hand, the coil spring 66 is accommodated in the small-diameter passage 62a and urges the tubular valve body 65 in the direction in which the intermediate branch passage 63 is opened.
The rear end of the bimetal spring 64 is locked by a stopper 67 to prevent the bimetal spring 64 from coming off from the in-shaft passage 62.
The bimetal spring 64 of this embodiment performs a shape change that extends at a high temperature above a predetermined temperature (for example, about 150 ° C.) and is longer than that at a low temperature.
Specifically, the bimetal spring 64 has the same configuration as the bimetal spring 52 of the first embodiment, and is a combination of materials having different expansion coefficients.
The urging force of the bimetal spring 64 is set to be smaller than the urging force of the coil spring 66 at a low temperature, and larger than the urging force of the coil spring 66 due to an increase in the urging force due to extension at a high temperature.

The cylindrical valve body 65 is a cylindrical valve body that has a through hole 65 a that passes through the center and communicates with the intermediate branch path 63, is fixed to the front end of the bimetal spring 64, and has a large-diameter passage in the in-axis passage 62. 62b.
The cylindrical valve body 65 is movable in the passage 62b so that the intermediate branch path 63 is closed at a low temperature and the intermediate branch path 63 and the through hole 65a are in communication at a high temperature.
In this embodiment, the lubricating oil passage 68 as the second passage is constituted by an opening-side passage 69a parallel to the rotary shaft 20 and a merging-side passage 69b from the opening-side passage 69a toward the spring accommodating portion 17.

In the compressor 60 of this embodiment, at a low temperature, as shown in FIG. 3A, the cylindrical valve body 65 opens the intermediate branch path 63, so that the lubricating oil entering the in-shaft path 62 from the crank chamber 16 It passes through the spring accommodating portion 17 from the in-shaft passage 62 and is further led out to the suction chamber 39 through the fixed throttle 46.
For this reason, the lubricating oil entering the lubricating oil passage 68 as the second passage and flowing out to the suction chamber 39 is relatively suppressed.
On the other hand, when the temperature is high (for example, 150 ° C. or more), as shown in FIG. 3B, the bimetal spring 64 extends, and the urging force of the bimetal spring 64 due to the extension closes the intermediate branch path 63. The cylindrical valve body 65 is moved against the coil spring 66.
While the intermediate branch path 63 is closed, the lubricating oil passage 68 communicates with the crank chamber 16 and the suction chamber 39, so that the lubricating oil excessively stored in the crank chamber 16 passes through the lubricating oil passage 68.
That is, since only the lubricating oil passage 68 is open, the lubricating oil flowing out to the suction chamber 39 through the lubricating oil passage 68 relatively increases.

According to this embodiment, when the tubular valve body 65 closes the intermediate branch path 63 at a high temperature, excess lubricating oil can be efficiently discharged only from the lubricating oil path 68.
That is, when the temperature in the crank chamber 16 is equal to or higher than the predetermined temperature, the first passage opening / closing mechanism 61 closes the intermediate branch passage 63, so that the lubricating oil in the crank chamber 16 is in the opened state. However, the lubricating oil can flow out from the crank chamber 16 to the suction chamber 39 more than when the intermediate branch path 63 is opened.

(Third embodiment)
Next, a compressor 70 according to a third embodiment will be described with reference to FIGS. 4 and 5.
Since most of the compressor 70 of this embodiment is common to the first embodiment, the same reference numerals are used for elements that are the same as or similar to those of the first embodiment, and the description of the first embodiment is given. Incorporate.
The compressor 70 of this embodiment includes a first passage formed mainly in the rotary shaft 20 and a second passage formed in the cylinder block 12 and joined to the first passage.
As shown in FIG. 4, the first passage is an in-axis passage 72 mainly provided in the rotary shaft 20.
The spring accommodating portion 17 in which the spring 32 is accommodated is a junction between the in-axis passage 72 serving as the first passage and the second passage.
The throttle is a fixed throttle 46 that communicates the spring accommodating portion 17 and the suction chamber 39.

An intermediate branch path 73 that communicates with the vicinity of the swash plate 26 of the crank chamber 16 is formed in the shaft path 72.
In this embodiment, the in-shaft passage 72 is composed of a small-diameter passage 72 a and a large-diameter passage 72 b, and the front end of the in-shaft passage 72 is not communicated with the shaft seal member accommodating portion 18, and The end communicates with the spring accommodating portion 17.
Accordingly, the in-shaft passage 72 as the first passage is a passage limited to the communication between the crank chamber 16 and the suction chamber 39.
The first passage of this embodiment is provided with a first passage opening / closing mechanism 71 as opening / closing means for opening / closing the intermediate branch path 73.
The first passage opening / closing mechanism 71 corresponds to an opening / closing means, and further includes a bimetallic coil spring 74 (hereinafter referred to as “bimetallic spring 74” for convenience) and a bimetallic spring 74 extending in the circumferential direction with a predetermined temperature as a boundary. It is mainly comprised from the cylindrical valve body 75 which opens and closes the intermediate branch path 73.
The bimetal spring 74 corresponds to an opening / closing member of the first passage opening / closing mechanism 71.
The bimetal spring 74 is accommodated in the in-shaft passage 72, and the rear end of the bimetal spring 74 is fixed by a retaining member 76 to prevent the bimetal spring 74 from coming off from the in-shaft passage 72 and to prevent rotation.

The bimetal spring 74 of this embodiment performs a shape change that extends in the circumferential direction at a high temperature equal to or higher than a predetermined temperature (for example, about 150 ° C.).
Specifically, as shown in FIG. 5A, the bimetal spring 74 is a combination of materials 74 a and 74 b having different expansion coefficients, and one material 74 a is formed in each part of the bimetal spring 74. The peripheral side always faces, and the other material 74b always faces the outer peripheral side.
For this reason, the front end of the bimetal spring 74 moves within a certain range in one circumferential direction when the temperature becomes high.

The cylindrical valve body 75 is a cylindrical valve body having a through hole 75 a passing through the center and a through hole 75 b communicating with the through hole 75 a and the intermediate branch path 73, and is accommodated in the in-axis passage 72.
The cylindrical valve body 75 is a valve body that closes the intermediate branch path 73 at a high temperature and communicates with the intermediate branch path 73 and the through hole 75a through a through hole 75b at a low temperature.
The cylindrical valve body 75 is fixed to the front end of the bimetal spring 74 and rotates in the circumferential direction of the in-axis passage 72 in accordance with the shape change of the bimetal spring 74 based on the temperature change.
In this embodiment, the lubricating oil passage 78 as the second passage is configured by an opening-side passage 79a parallel to the rotation shaft 20 and a merging-side passage 79b from the opening-side passage 79a toward the spring accommodating portion 17. The opening 78 a of the lubricating oil passage 78 faces the crank chamber 16.

In the compressor 60 of this embodiment, when the temperature is low, as shown in FIG. 4, the cylindrical valve body 75 opens the intermediate branch path 73, so that the lubricating oil entering the in-shaft passage 72 from the crank chamber 16 is transferred to the in-shaft passage. 72 passes through the spring accommodating portion 17 and is further led to the suction chamber 39 through the fixed throttle 46.
For this reason, the lubricating oil entering the lubricating oil passage 78 as the second passage and flowing out to the suction chamber 39 is relatively suppressed.
On the other hand, when the temperature is high (for example, 150 ° C. or higher), as shown in FIG. 5B, the bimetal spring 74 extends in the circumferential direction, and the front end of the bimetal spring 74 that extends in the circumferential direction is an intermediate branch path. The cylindrical valve body 75 is rotated so as to close 73.
While the intermediate branch path 73 is closed, the lubricating oil passage 78 communicates between the crank chamber 16 and the suction chamber 39, so that the lubricating oil excessively stored in the crank chamber 16 passes through the lubricating oil passage 78.
That is, since only the lubricating oil passage 78 is open, the lubricating oil flowing out to the suction chamber 39 through the lubricating oil passage 78 relatively increases.
According to this embodiment, the same or similar effect as that of the second embodiment can be obtained.

(Fourth embodiment)
Next, the compressor 80 according to the second embodiment will be described with reference to FIGS. 6 and 7.
Since most of the compressor 80 of this embodiment is common to the first embodiment, the same reference numerals are used for elements that are the same as or similar to those of the first embodiment, and the description of the first embodiment is given. Incorporate.
In the compressor 80 of this embodiment, as shown in FIG. 6, a passage for extracting the refrigerant in the crank chamber 16 to the suction chamber 39, that is, an extraction passage is provided.
The extraction passage of this embodiment mainly includes a first passage, a second passage having a different route from the first passage and joining the second passage, a joining portion of the first passage and the second passage, a joining portion, A throttle formed between the suction chamber 39 and the suction chamber 39 is included.
Specifically, as shown in FIG. 6, the first passage is an in-shaft passage 45 provided mainly in the rotary shaft 20.
The spring accommodating portion 17 in which the spring 32 is accommodated is a joining portion between the in-shaft passage 45 serving as the first passage and the second passage.
The throttle is a fixed throttle 46 that communicates the spring accommodating portion 17 and the suction chamber 39.
The front end of the in-shaft passage 45 communicates with the shaft seal member accommodating portion 18, and the rear end communicates with the spring accommodating portion 17.
An intermediate branch passage 47 communicating with the vicinity of the swash plate 26 of the crank chamber 16 is formed in the middle of the in-shaft passage 45.

Next, referring to the second passage, the second passage in this embodiment is a lubricating oil passage 81 that has an opening 82 a near the peripheral wall 12 b of the cylinder block 12 and merges with the spring accommodating portion 17.
The lubricating oil passage 81 includes an opening-side passage 82 that is parallel to the axis of the rotary shaft 20 and a merging-side passage 83 that leads from the opening-side passage 82 to the spring accommodating portion 17.
A connecting portion between the opening side passage 82 and the merging side passage 83 is provided with a second passage opening / closing mechanism 84 that opens and closes the lubricating oil passage 81.
As shown in FIGS. 7A and 7B, the second passage opening / closing mechanism 84 of this embodiment includes a shape memory spring 85 made of a shape memory alloy whose shape changes with a predetermined temperature as a boundary, and a shape memory spring. It is mainly composed of a spherical valve body 86 that opens and closes the lubricating oil passage 81 by changing its shape.
The shape memory spring 85 corresponds to an opening / closing member of the second passage opening / closing mechanism 84.

The shape memory spring 85 is accommodated in an opening / closing means accommodating portion 87 formed rearward from the opening side passage 82.
The shape memory spring 85 of this embodiment is in an extended state as shown in FIG. 7A, for example, when the temperature is lower than a predetermined temperature (for example, about 150 ° C.), and when the temperature is higher than the predetermined temperature, FIG. As shown in b), the shape change is shortened more than at low temperatures.
A valve body 86 facing the connecting portion between the opening side passage 82 and the merging side passage 83 is attached to the end of the shape memory spring 85, and the valve body 86 is moved to the opening side passage 82 by the elastic force of the shape memory spring 85 at low temperatures. The urged valve body 86 blocks the opening-side passage 82 in the connection portion.
Further, when the shape memory spring 85 is shortened at a high temperature, the valve body 86 can open the opening-side passage 82 in the connection portion.

In the compressor 80 of this embodiment, the second passage opening / closing mechanism 84 opens the lubricating oil passage 81 when the temperature in the crank chamber 16 reaches a predetermined temperature (for example, about 150 ° C.) or higher.
Specifically, when the temperature in the crank chamber 16 exceeds a predetermined temperature, the shape memory spring 85 is shortened, and the shortening of the shape memory spring 85 causes the valve body 86 to open on the opening side passage in the lubricating oil passage 48. Open 82.
By opening the opening side passage 82, the opening side passage 82 and the merging side passage 83 communicate with each other, and the lubricating oil excessively stored in the crank chamber 16 can be passed to the lubricating oil passage 81.
The excessively stored lubricating oil in the crank chamber 16 is caused by the differential pressure between the crank chamber 16 and the suction chamber 39 and the centrifugal force due to the rotation of the rotating elements in the crank chamber 16 including the swash plate 26 and the rotating shaft 20. It passes through the lubricating oil passage 81 and flows out from the spring accommodating portion 17 to the suction chamber 39 through the fixed throttle 46.

The excess lubricating oil flowing out from the crank chamber 16 through the lubricating oil passage 81 reduces the lubricating oil in the crank chamber 16 and reduces the shear friction due to the stirring between the lubricating oil and the swash plate 26.
By reducing the shear friction between the lubricating oil and the swash plate 26, heat generation due to the shear friction is suppressed, and the temperature rise in the crank chamber 16 is suppressed.
When the temperature rise is suppressed and the temperature in the crank chamber 16 falls below a predetermined temperature, the shape memory spring 85 extends and the valve body 53 closes the opening side passage 82 in the lubricating oil passage 81.
When the lubricating oil passage 82 is closed by the second passage opening / closing mechanism 84, at least the lubricating oil required by the sliding portion in the crank chamber 16 remains in the crank chamber 16.

Thus, for example, when the compressor in which the excessive amount of lubricating oil is stored in the crank chamber 16 rotates at a high speed, the excessive lubricating oil is discharged from the crank chamber 16 through the lubricating oil passage 81, and the swash plate 26. Heat generation due to shear friction with excess lubricating oil is suppressed.
On the other hand, in the compressor 10 in which the lubricating oil is excessively stored in the crank chamber 16, when the swash plate 26 rotates at a low speed, the lubricating oil is sufficiently retained in the crank chamber 16, and the sliding portion in the crank chamber 16 is retained. Is ensured without a shortage of necessary lubricating oil.
According to the compressor 80 according to this embodiment, since the second passage is provided with the second passage opening / closing mechanism 84, the same effect as that of the first embodiment is obtained.

(Fifth embodiment)
Next, the compressor 90 according to the second embodiment will be described with reference to FIG.
Since most of the compressor 90 of this embodiment is common to the first embodiment, the same reference numerals are used for elements that are the same as or similar to those of the first embodiment, and the description of the first embodiment is given. Incorporate.
In addition, since a part of the configuration is the same as that of the fourth embodiment, the same reference numerals used in the fourth embodiment are used in common for the common elements.
As shown in FIG. 8, the compressor 90 of this embodiment includes a communication path 92 as a first path that connects the crank chamber 16 and the suction chamber 39 to the cylinder block 12, and a lubricating oil path 81 as a second path. The lubricating oil passage 81 is joined to the communication passage 92 to form a joining portion 94.
A fixed throttle 95 is provided between the junction 94 and the suction chamber 39, and the fixed throttle 95 sets a differential pressure between the crank chamber 16 and the suction chamber 39.

The lubricating oil passage 81 is provided with a shape memory spring 85 as an opening / closing member and an opening / closing means 84 by a spherical valve body 86, and when the temperature of the crank chamber 16 rises to exceed a predetermined temperature, the lubricating oil A means for opening the passage 81 is provided.
In this embodiment, an oil separator 68 that separates the lubricating oil from the high-pressure refrigerant in the discharge chamber 40 is provided in the external refrigerant circuit 96, and the supply path that supplies the lubricating oil separated by the oil separator 97 to the crank chamber 16. 98 is provided.
By supplying the lubricating oil of the oil separator 97 to the crank chamber 16, for example, the lubricating oil required in the crank chamber 16 can be secured at low speed.

(Another example of the second passage opening and closing mechanism)
Next, another example of the second passage opening / closing mechanism for opening and closing the lubricating oil passage will be described with reference to FIG.
The second passage opening / closing mechanism 102 shown in FIG. 9A includes a valve body 103 that opens and closes the lubricating oil passage 101 that communicates the crank chamber 16 and the suction chamber 39, a normal spring 104 that biases the valve body 103, And a bimetal regulating member 105 that regulates the position of the valve body 103.
When the temperature in the crank chamber 16 rises so as to exceed a predetermined temperature, the restricting member 105 made of bimetal is deformed, and the valve element 74 opens the lubricating oil passage 71 by the bias of the spring 104.

The second passage opening / closing mechanism 112 according to another example will be described. The second passage opening / closing mechanism 112 shown in FIG. 9B includes a temperature sensor 113 as a temperature detector and an opening / closing tool for opening / closing the lubricating oil passage 111. 114, an actuator 115 that moves the opening / closing tool 114 forward and backward based on the output of the temperature sensor 113, and a controller 116 that controls the actuator 115 based on the output of the temperature sensor 113.
Even when the second passage opening / closing mechanisms 102 and 112 shown in FIGS. 9A and 9B are used, the temperature in the crank chamber 16 exceeds the predetermined temperature as in the first embodiment. In the case of rising, the lubricating oil passages 101 and 111 can be opened.

(Sixth embodiment)
Next, the compressor 120 according to the sixth embodiment will be described.
Since most of the compressor 90 of this embodiment is common to the first embodiment, the same reference numerals are used for elements that are the same as or similar to those of the first embodiment, and the description of the first embodiment is given. Incorporate.
In addition, since part of the configuration is common to the fourth embodiment and another example of the second passage opening / closing mechanism, common elements are used in the fourth embodiment and another example of the second passage opening / closing mechanism. The code is used in common.
In the compressor of this embodiment, as shown in FIG. 10, a communication passage 92 as a first passage for communicating the crank chamber 16 and the suction chamber 39 with the cylinder block 12 and a lubricating oil passage 81 as a second passage are formed. Then, the lubricating oil passage 81 joins the communication passage 92 to form a joining portion 94.
The first passage is provided with a first passage opening / closing mechanism 121 that opens and closes the first passage, and the second passage is also provided with a second passage opening / closing mechanism 84 that opens and closes the second passage.
That is, in this embodiment, the opening / closing means includes the first passage opening / closing mechanism 121 and the second passage opening / closing mechanism 84.

The first passage opening / closing mechanism 121 regulates the position of the valve body 103 that opens and closes the communication passage 92 that connects the crank chamber 16 and the suction chamber 39, the normal spring 104 that biases the valve body 103, and the valve body 103. And a restriction member 105 made of bimetal.
When the temperature in the crank chamber 16 becomes equal to or higher than a predetermined temperature (for example, about 150 ° C.), the bimetal regulating member 105 is deformed, and the valve element 74 closes the communication path 92 by the urging of the spring 104, The member 105 corresponds to the opening / closing member of the first passage opening / closing mechanism 121.
On the other hand, the second passage opening / closing mechanism 84 opens and closes the shape memory spring 85 made of a shape memory alloy whose shape changes at a predetermined temperature (for example, about 150 ° C.) and the lubricating oil passage 81 by the shape change of the shape memory spring 85. The shape memory spring 85 corresponds to an opening / closing member of the second passage opening / closing mechanism 84.

According to this embodiment, when the temperature of the crank chamber 16 is equal to or lower than the predetermined temperature, only the first passage facing the region where the density of the lubricating oil in the crank chamber 16 is low is opened, so that the lubricating oil flows into the suction chamber 39. In addition, the necessary lubricating oil can be sufficiently stored in the crank chamber 16, and when the temperature of the crank chamber 16 is equal to or higher than a predetermined temperature, only the second passage facing the dense region in the crank chamber 16 is provided. Since the opening is opened, the lubricating oil can be sufficiently discharged from the crank chamber to the suction chamber without excessively storing the lubricating oil in the crank chamber 16.
In addition, since the opening / closing means includes the first passage opening / closing mechanism 121 and the second passage opening / closing mechanism 84, for example, the ratio of the lubricating oil flow rate passing through the first passage and the second passage can be set according to the temperature. It becomes.

The present invention is not limited to the above-described embodiment, and various modifications are possible within the scope of the gist of the invention. For example, the following modifications may be made.
In the above first to sixth embodiments, the fixed throttle is provided as the throttle, but for example, a variable throttle using a control valve or the like may be provided.
○ In the first to fourth embodiments described above, an intermediate branch path is provided in the in-shaft path as the first path, and the intermediate branch path is shut off when the compressor is operated at the minimum capacity. Regardless of the operating state, an intermediate branch passage in which the crank chamber and the in-shaft passage are always in communication may be provided, and the position provided on the rotating shaft is also free.
In the first to sixth embodiments, the lubricating oil passage is formed in the cylinder block. For example, if the lubricating oil passage merges with the first passage, such as piping the lubricating oil passage outside the housing, The lubricating oil passage is not prevented from being provided other than the cylinder block.
In the second embodiment, the bimetal spring 64 and the coil spring 66 are provided in the in-axis passage. However, another bimetal spring may be used instead of the coil spring 66. In this case, another bimetal spring is used. Needs to be a bimetal spring that expands at a low temperature and increases its urging force.
In the above sixth embodiment, the temperature at which the opening and closing of the first passage and the second passage is switched is set to a predetermined temperature (for example, about 150 ° C.), but the temperature at which the opening and closing of the first passage is switched and the second passage The switching temperatures may be different from each other. In this case, the temperature at which the opening and closing of the first passage is switched is preferably higher than the temperature at which the second passage is switched.

It is sectional drawing which shows the outline | summary of the variable displacement compressor which concerns on 1st Embodiment. It is principal part sectional drawing which shows the 2nd channel | path opening / closing mechanism and bimetal spring of 1st Embodiment. It is principal part sectional drawing of the variable capacity type compressor which concerns on 2nd Embodiment. It is principal part sectional drawing of the variable displacement compressor which concerns on 3rd Embodiment. It is principal part sectional drawing which shows the bimetal spring and 2nd channel | path opening / closing mechanism of 3rd Embodiment. It is sectional drawing which shows the outline | summary of the variable capacity type compressor which concerns on 4th Embodiment. It is principal part sectional drawing which shows the 2nd channel | path opening / closing mechanism of 4th Embodiment. It is sectional drawing which shows the outline | summary of the compressor which concerns on 5th Embodiment. It is principal part sectional drawing which shows another example of a 2nd channel | path opening / closing mechanism. It is sectional drawing which shows the outline | summary of the compressor which concerns on 6th Embodiment.

Explanation of symbols

10, 60, 70, 80, 90, 120 Compressor 16 Crank chamber 17 Spring housing portion 18 Shaft seal member housing portion 20 Rotating shaft 26 Swash plate 33 Piston 39 Suction chamber 40 Discharge chamber 44 Capacity control valves 45, 62, 72 Shaft Inner passages 47, 63, 73 Intermediate branch passages 46, 95 Fixed restrictors 48, 68, 81, 101, 111 Lubricating oil passages 49, 69a, 82 Open side passages 50, 69b, 83 Merge side passages 51, 84, 102, 112 Second passage opening / closing mechanism 52, 64, 74 Bimetal springs 53, 65, 75 Cylindrical valve bodies 61, 71, 121 First passage opening / closing mechanism 85 Shape memory spring 86, 103 Valve body 92 Communication passage 94 Merging portion 97 Oil separator 105 Regulating member 114

Claims (8)

A suction chamber for sucking low-pressure refrigerant from the outside; a compression chamber for compressing the refrigerant; a discharge chamber for discharging the compressed high-pressure refrigerant; a crank chamber for housing a swash plate that rotates together with a rotating shaft; In a variable displacement compressor comprising an air supply passage connecting the crank chamber and the discharge chamber, and a bleed passage connecting the suction chamber and the crank chamber, the discharge capacity being variable based on pressure fluctuations in the crank chamber ,
The extraction passage includes a first passage communicating with the crank chamber;
A second passage that communicates with the crank chamber in a different path from the first passage and that is formed on the outer peripheral side of the first passage in the radial direction of the rotating shaft;
A junction where the first passage and the second passage join each other;
Including a throttle formed between the junction and the suction chamber;
Opening and closing means for opening and closing at least one of the first passage and the second passage;
The variable capacity compressor, wherein the second passage is opened when a temperature in the crank chamber is equal to or higher than a predetermined temperature. The opening / closing means has a first passage opening / closing mechanism for opening / closing the first passage, and the first passage opening / closing mechanism closes the first passage when a temperature in the crank chamber is equal to or higher than a predetermined temperature. The variable capacity compressor according to claim 1. The opening / closing means has a second passage opening / closing mechanism for opening / closing the second passage, and the second passage opening / closing mechanism opens the second passage when the temperature in the crank chamber is equal to or higher than a predetermined temperature. The variable capacity compressor according to claim 1. The opening / closing means has a first passage opening / closing mechanism for opening / closing the first passage and a second passage opening / closing mechanism for opening / closing the second passage, and when the temperature of the crank chamber is lower than a predetermined temperature, When the first passage opening / closing mechanism opens the first passage, the second passage opening / closing mechanism closes the second passage, and when the temperature of the crank chamber is equal to or higher than a predetermined temperature, the first passage opening / closing mechanism opens the first passage. The variable capacity compressor according to claim 1, wherein the second passage opening and closing mechanism opens the second passage. 5. The variable capacity type according to claim 1, wherein the second passage has an opening facing the crank chamber, and the opening is disposed near a peripheral wall of the crank chamber. Compressor. The variable capacity compressor according to any one of claims 1 to 5, wherein the opening / closing means includes an opening / closing member formed of a bimetal or a shape memory alloy. The said opening / closing means includes a temperature detecting body for detecting the temperature in the crank chamber, and an opening / closing tool that is controlled to open and close based on a detection output of the temperature detecting body. Variable capacity compressor. The variable capacity compressor according to any one of claims 1 to 7, wherein the first passage includes an in-shaft passage formed inside the rotating shaft.

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