JP2009287421A - Variable displacement swash plate compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement swash plate compressor capable of preventing run-out of lubricating oil in an oil storage chamber, and capable of supplying the lubricating oil in a suitable amount in accordance with a delivery flow rate of a refrigerant. <P>SOLUTION: A valve means for controlling an opening of an oil passage 50 guiding the lubricating oil in the oil storage chamber 37 to an intake chamber 32 is provided with a valve chamber 42, a valve element 44 sliding in the valve chamber 42, and a spring 45 energizing the valve element 44. The valve chamber 42 is partitioned into a first valve chamber 46 communicated with an intake passage 38 so that a static pressure Ps1 and a dynamic pressure Ps2 of the refrigerant flowing in the intake passage 38 is introduced and a second valve chamber 47 communicated with a crank chamber 16 by the valve element 44, and the spring 45 is arranged in the first valve chamber 46 so as to energize the valve element 44 to the second valve chamber 47 side. An opening part 50a of the oil passage 50 is provided on a sliding surface 54 with the valve element 44 in the valve chamber 42, and a communication passage 53 communicating the oil passage 50 and the first valve chamber 46 and having a passage cross sectional area S2 smaller than a passage cross sectional area S1 of the oil passage 50 is provided on the valve element 44. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a variable capacity swash plate compressor incorporating an oil separator mainly used for vehicle air conditioning.

For example, in the prior art disclosed in Patent Document 1, an oil separation chamber having an oil separation mechanism is provided in a high-pressure region communicated with a discharge chamber, and lubricating oil is stored below the oil separation chamber. The storage chamber is formed. The storage chamber is connected to two oil supply passages for circulating the lubricating oil in the storage chamber to the swash plate chamber, and a differential pressure valve is provided between the two oil supply passages.
The differential pressure valve has a stepped hole-like valve chamber and a step-like spool fitted and inserted into the valve chamber, and seals provided on the large-diameter portion and the small-diameter portion of the spool, An oil passage is formed between the outer peripheral surface of the spool. And the two oil supply paths are connected via the oil path. The small diameter side of the valve chamber communicates with the suction chamber, and the large diameter side of the valve chamber communicates with the compression chamber.

During operation of the compressor, the compression chamber pressure introduced to the large diameter side of the valve chamber is high, overcoming the resultant force of the suction pressure introduced to the small diameter side of the valve chamber and the discharge pressure acting on the step surface, The spool moves to the small diameter side. Thus, both the oil supply passages and the oil passages are communicated with each other, and the lubricating oil in the storage chamber is supplied to the swash plate chamber via both oil supply passages.
On the other hand, when the operation of the compressor is stopped, the compression chamber pressure is reduced to substantially the same as the suction pressure, so that the discharge pressure acting on the step surface becomes dominant, and the spool moves to the larger diameter side. As a result, the communication between the downstream oil supply passage and the oil passage is blocked, and the supply of lubricating oil from the storage chamber to the swash plate chamber is stopped.
Accordingly, the supply of the lubricating oil from the storage chamber to the swash plate chamber can be turned on only during the operation of the compressor, and can be turned off while the compressor is stopped. Inflow is prevented, and problems due to oil compression in the swash plate chamber can be prevented.
Japanese Unexamined Patent Publication No. 2000-27756 (pages 3 to 4, FIGS. 1 to 3)

  However, in the prior art disclosed in Patent Document 1, the supply of lubricating oil from the storage chamber to the swash plate chamber is controlled ON and OFF in accordance with the operation and stoppage of the compressor. The supply amount of the lubricating oil is constant regardless of the refrigerant discharge flow rate. In particular, when the compressor is a variable capacity type compressor that is used while changing the capacity according to the size of the cooling load, there are the following problems. In other words, the supply amount of the lubricating oil is constant regardless of the refrigerant discharge flow rate. Therefore, even if a proper amount of lubricating oil is supplied during the large capacity operation, the supply of the lubricating oil during the small capacity operation is performed. There is a risk of problems such as exhaustion of lubricating oil in the storage chamber due to excessive amount.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to prevent the lubricating oil in the oil storage chamber from being depleted and to supply an appropriate amount of lubricating oil according to the refrigerant discharge flow rate. To provide a variable displacement swash plate compressor.

  In order to achieve the above object, according to the first aspect of the present invention, an oil storage chamber for storing lubricating oil separated from the discharge gas is provided in the housing of the compressor, and the lubricating oil stored in the oil storage chamber is guided into the compressor. In the variable capacity swash plate compressor provided with valve means for controlling the opening degree of the oil passage, the valve means is provided in communication with the suction passage for introducing the refrigerant into the suction chamber and the crank chamber, respectively. A chamber, a valve body slidably provided in the valve chamber, and a biasing member that biases the valve body. The valve chamber communicates with the suction passage by the valve body. A first valve chamber into which a static pressure and a dynamic pressure of the refrigerant flowing in the chamber are introduced, and a second valve chamber communicating with the crank chamber; the biasing member is disposed in the valve chamber; The body is urged toward the second valve chamber, and the sliding surface with the valve body in the valve chamber is An opening of the oil passage that connects the valve chamber and the oil storage chamber is provided, and the oil passage and the first valve chamber or the second valve chamber communicate with the valve body or the sliding surface. A connecting passage is provided, and the valve body slides in the valve chamber on the basis of the respective pressure differences received from the first valve chamber and the second valve chamber, thereby opening the opening of the oil passage during maximum capacity operation. Becomes the maximum state, the opening degree of the oil passage becomes the minimum state during the minimum capacity operation, and the oil passage and the first valve chamber or the second valve chamber are smaller than the passage cross-sectional area of the oil passage during the variable capacity operation. The opening degree of the oil passage is controlled so as to communicate with the communication passage having a passage cross-sectional area.

According to the first aspect of the present invention, the refrigerant suction pressure (static pressure + dynamic pressure) is applied to the surface of the first valve chamber communicated with the suction passage of the valve body in the second valve chamber communicated with the crank chamber. Crank chamber pressure acts on the surface, and the valve element is urged toward the second valve chamber by the urging member.
Therefore, the valve body can move in the valve chamber according to the balance between the differential pressure between the suction pressure (static pressure + dynamic pressure) and the crank chamber pressure (static pressure) and the urging force of the urging member. .
During maximum capacity operation, the crank chamber pressure (static pressure) is almost equal to the suction pressure (static pressure), but the suction pressure (dynamic pressure) and the biasing force of the biasing member act on the valve body. It moves greatly to the two-valve chamber side, and the opening of the oil passage becomes the maximum. Thus, the lubricating oil stored in the oil storage chamber is supplied into the compressor through the oil passage, and the sliding portion of the compressor can be sufficiently lubricated.
Further, during the minimum capacity operation, the crank chamber pressure (static pressure) is almost equal to the suction pressure (static pressure), and the suction pressure (dynamic pressure) hardly acts. It moves to the two-valve chamber side and the opening of the oil passage becomes the minimum state. In addition, the minimum state here means a state including a fully closed state in which the opening degree is zero. Thus, the lubricating oil stored in the oil storage chamber is hardly or completely supplied into the compressor through the oil passage, and it is possible to prevent depletion of the lubricating oil in the oil storage chamber.
Further, during variable displacement operation, the crank chamber pressure (static pressure) is higher than the suction pressure (static pressure + dynamic pressure), so that the valve body has a biasing member that biases the valve body toward the second valve chamber side. The pressing force based on the differential pressure that presses the valve element toward the first valve chamber side acts more preferentially than the urging force, and the valve element moves largely toward the first valve chamber side so that the oil passage and the first valve chamber or The second valve chamber communicates with the second passage. As a result, the lubricating oil stored in the oil storage chamber is guided to the first valve chamber or the second valve chamber through the oil passage and the communication passage, and is supplied to the suction chamber or the crank chamber. Since the passage sectional area of the passage is smaller than the passage sectional area of the oil passage, the supply amount of the lubricating oil is reduced by the communication passage. Thus, during variable displacement operation, an appropriate amount of lubricating oil narrowed down by the communication passage can be supplied to the suction chamber or the crank chamber.
Therefore, it is possible to supply an appropriate amount of lubricating oil according to the refrigerant discharge flow rate, that is, the operation state of the compressor, and it is possible to prevent the lubricating oil from being depleted in the oil storage chamber.

According to a second aspect of the present invention, in the variable displacement swash plate compressor according to the first aspect, the communication passage includes an outer circumferential groove formed on an outer circumferential surface of the valve body over the entire circumference, and the outer circumferential groove is disposed on the outer circumferential groove. It is formed by the through-hole connected to one valve chamber.
According to the second aspect of the present invention, even when the valve body rotates in the circumferential direction in the valve chamber, the lubricating oil is reliably guided from the oil passage to the through hole through the outer circumferential groove formed over the entire circumference, and the first valve Lubricating oil can be supplied to the suction chamber through the chamber.

According to a third aspect of the present invention, in the variable displacement swash plate compressor according to the first aspect, the communication passage is a notch formed on an outer peripheral surface of the valve body and opening to the second valve chamber side. It is characterized by.
According to the third aspect of the present invention, the lubricating oil is supplied from the oil passage to the second valve chamber side through the notch, and the lubricating oil is supplied to the crank chamber through the passage communicating the second valve chamber and the crank chamber. Is possible. Moreover, since it is only necessary to form a notch on the outer peripheral surface of the valve body, the number of manufacturing steps can be reduced.

According to a fourth aspect of the present invention, in the variable displacement swash plate compressor according to the first aspect, the communication passage is formed on the sliding surface so as to communicate with an opening of the oil passage, and the variable passage swash plate compressor is configured to perform the first operation during variable displacement operation. It is characterized by a notch opening to the two-valve chamber side.
According to invention of Claim 4, it is possible to supply lubricating oil to the 2nd valve chamber side from an oil passage through a notch. In addition, since the outer peripheral surface of the valve body does not require processing, the number of manufacturing steps can be reduced.

  According to the present invention, the communication passage is provided in the valve body or the sliding surface, and the oil passage and the communication passage are communicated during variable displacement operation, so that an appropriate amount of lubrication can be obtained according to the refrigerant discharge flow rate, that is, the operation state. Oil can be supplied, and exhaustion of lubricating oil in the oil storage chamber can be prevented.

(First embodiment)
A variable capacity swash plate compressor (hereinafter simply referred to as “compressor”) according to a first embodiment will be described below with reference to FIGS.
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. For convenience of explanation, the left side of the compressor 10 in FIG.
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 defined by the front housing 13 and the cylinder block 12.
A drive shaft 17 is provided in the housing 11 so as to pass through the vicinity of the center of the crank chamber 16. The drive shaft 17 is provided in a radial bearing 18 provided in the front housing 13 and in the cylinder block 12. The other radial bearing 19 is rotatably supported.
A shaft seal device 20 is provided in front of the radial bearing 18 that supports the front portion of the drive shaft 17 so as to be in sliding contact with the circumferential surface of the drive shaft 17. The front end of the drive shaft 17 in this embodiment is connected to an external drive source via a power transmission mechanism (not shown).

A lug plate 21 as a rotating body is fixed to the drive shaft 17 in the crank chamber 16 so as to be integrally rotatable.
A swash plate 22 constituting a capacity changing mechanism is supported on the drive shaft 17 behind the lug plate 21 so as to be slidable and tiltable in the axial direction of the drive shaft 17.
A hinge mechanism 23 is interposed between the swash plate 22 and the lug plate 21, and the swash plate 22 is connected to the lug plate 21 and the drive shaft 17 through the hinge mechanism 23 so as to be capable of synchronous rotation and tilting. ing.

A coil spring 24 is wound between the lug plate 21 and the swash plate 22 of the drive shaft 17 and is urged rearward by the pressing of the coil spring 24 so as to be slidable with respect to the drive shaft 17. A body 25 is fitted on the drive shaft 17.
The swash plate 22 is always pressed backward, that is, in a direction in which the inclination angle of the swash plate 22 decreases, by the cylindrical body 25 that receives the urging force of the coil spring 24. Here, the inclination angle of the swash plate 22 means an angle formed by a surface orthogonal to the drive shaft 17 and a surface of the swash plate 22.

  A stopper portion 22a projects from the front portion of the swash plate 22, and the maximum inclination angle position of the swash plate 22 is defined by the stopper portion 22a coming into contact with the lug plate 21. A retaining ring 26 is attached to the drive shaft 17 behind the swash plate 22, and a coil spring 27 is wound around the drive shaft 17 in front of the retaining ring 26. When the swash plate 22 abuts against the front portion of the coil spring 27, the minimum inclination angle position of the swash plate 22 is defined. In FIG. 1, the swash plate 22 is at the maximum tilt angle position.

Each cylinder bore 12a of the cylinder block 12 accommodates a single-headed piston 28 so as to be able to reciprocate. The front ends of these pistons 28 are engaged with the outer periphery of the swash plate 22 via a pair of shoes 29. .
When the swash plate 22 is rotated synchronously with the drive shaft 17 as the drive shaft 17 rotates, each piston 28 is reciprocated in the cylinder bore 12a through the shoe 29 in the front-rear direction.

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 with a valve plate 31 interposed therebetween.
A suction chamber 32 is formed on the center side in the rear housing 14, and a discharge chamber 33 is formed on the outer peripheral side in the rear housing 14. The suction chamber 32 and the discharge chamber 33 are respectively connected to the compression chamber 30 in the cylinder bore 12a by a suction port 31a and a discharge port 31b provided in the valve plate 31. The suction port 31a and the discharge port 31b are provided with a suction valve 31c and a discharge valve 31d, respectively.
By the way, when each piston 28 moves from the top dead center position to the bottom dead center position, the refrigerant gas in the suction chamber 32 is sucked into the compression chamber 30 in the cylinder bore 12a through the suction port 31a. The refrigerant gas sucked into the compression chamber 30 is compressed to a predetermined pressure by movement from the bottom dead center position of the piston 28 to the top dead center position, and is discharged to the discharge chamber 33 through the discharge port 31b.

In the compressor 10, a capacity control valve 34 is provided in the rear housing 14 in order to adjust the stroke of the piston 28, that is, the discharge capacity of the compressor 10 by changing the inclination angle of the swash plate 22. .
The capacity control valve 34 is disposed in the middle of an air supply passage 35 that connects the crank chamber 16 and the discharge chamber 33. The cylinder block 12 is formed with an extraction passage 36 that communicates the crank chamber 16 and the suction chamber 32.
The amount of high-pressure refrigerant gas introduced from the discharge chamber 33 into the crank chamber 16 through adjustment of the valve opening of the capacity control valve 34 and the amount of refrigerant gas to be led out from the crank chamber 16 to the suction chamber 32 through the extraction passage 36. The pressure in the crank chamber 16 is determined by the balance with the derived amount.
As a result, the pressure difference between the crank chamber 16 and the compression chamber 30 sandwiching the piston 28 is changed, and the inclination angle of the swash plate 22 is changed.

By the way, as shown in FIG. 1, an oil storage chamber 37 in which lubricating oil is stored is formed in the upper outer periphery of the cylinder block 12.
Mist oil contained in the high-pressure refrigerant gas discharged from the discharge chamber 33 is separated into lubricating oil and gas by an oil separator (not shown), and the lubricating oil is stored in the oil storage chamber 37. The oil separator is installed in a refrigerant gas passage (not shown) connecting the discharge chamber 33 and the high-pressure side of the external refrigerant circuit (not shown).

The rear housing 14 is formed with a bottomed round hole-shaped suction passage 38 extending in the vertical direction, and a suction port 39 is formed at an opening to the outside of the suction passage 38. The suction port 39 is connected to the low pressure side of an external refrigerant circuit (not shown). The suction passage 38 communicates with the suction chamber 32 via the suction port 40. The refrigerant gas introduced into the suction passage 38 via the suction port 39 is sucked into the suction chamber 32 through the suction port 40.
A valve chamber 42 is provided below the suction passage 38 in communication with the suction passage 38, and the valve chamber 42 and the suction passage 38 are partitioned by a partition wall 41. The partition wall 41 is provided with a hole 43 that connects the valve chamber 42 and the suction passage 38. A cylindrical valve body 44 is disposed in the valve chamber 42 so as to be movable in the vertical direction.

As shown in FIGS. 1 and 2, the valve chamber 42 is partitioned by a valve body 44, and a first valve chamber 46 on the suction passage 38 side and a second valve chamber 47 on the side opposite to the suction passage 38 with respect to the valve body 44. It is divided into. The first valve chamber 46 and the suction passage 38 communicate with each other through the hole 43, and the static pressure and dynamic pressure of the refrigerant flowing in the suction passage 38 are introduced into the first valve chamber 46. Further, the second valve chamber 47 and the crank chamber 16 are communicated with each other through a passage 49. A spring 45 is mounted in the first valve chamber 46 as a biasing member that biases the valve body 44 toward the second valve chamber 47.
The valve chamber 42 and the oil storage chamber 37 are connected via an oil passage 50.

As shown in FIGS. 2 and 3, the valve body 44 communicates with the first valve chamber 46 through the outer circumferential groove 51 having a U-shaped cross section formed on the entire outer circumferential surface of the valve body 44 and the outer circumferential groove 51. The through-hole 52 to be formed is formed, and the outer circumferential groove 51 and the through-hole 52 constitute a communication passage 53.
Here, if the passage sectional area of the oil passage 50 is S1, and the passage sectional area of the through hole 52 is S2, S1> S2.
An opening 50 a of the oil passage 50 that connects the oil storage chamber 37 and the valve chamber 42 is provided on a sliding surface 54 with the valve body 44 in the valve chamber 42.

  As shown in FIG. 2, the valve body 44 controls the opening degree of the oil passage 50 by moving up and down in the valve chamber 42. That is, when the valve body 44 is moved down most and comes into contact with the bottom of the valve chamber 42 (lower limit position), the upper end surface of the valve body 44 is positioned below the opening 50a of the oil passage 50 and the oil passage. The opening 50a of the oil passage 50 is in the fully open state, and when the valve body 44 rises most and comes into contact with the lower end of the partition wall 41 (upper limit position), the opening 50a of the oil passage 50 and the outer peripheral groove 51 communicate with each other. When the valve body 44 is at an intermediate position between the lower limit position and the upper limit position, the opening 50a of the oil passage 50 is set to be in a minimum state by being blocked by the outer peripheral surface of the valve body 44. In FIG. 2, the valve body 44 indicated by a solid line is in the lower limit position. At this time, a protrusion is provided at the bottom, and the valve body 44 abuts on the protrusion to contact the bottom of the valve chamber 42 and the valve body. A gap is formed between the two and 44. Moreover, the valve body 44 shown with a dashed-two dotted line exists in an upper limit position.

  Here, the suction pressure of the refrigerant flowing through the suction passage 38 is Ps (total pressure) = static pressure Ps1 + dynamic pressure Ps2, the suction chamber pressure of the suction chamber 32 is Pt, the crank chamber pressure of the crank chamber 16 is Pc, If the valve chamber pressure of the first valve chamber 46 is Pv1, and the valve chamber pressure of the second valve chamber 47 is Pv2, the valve chamber pressure Pv1 is substantially equal to the suction pressure Ps (total pressure), and the valve chamber pressure Pv2 is It becomes almost equal to the crank chamber pressure Pc. Therefore, the suction pressure Ps (total pressure) acts on the upper surface of the first valve chamber 46 and the crank chamber pressure Pc acts on the lower surface of the second valve chamber. 44 is urged toward the second valve chamber 47 side. Accordingly, the valve body 44 moves up and down in the valve chamber 42 in accordance with the balance between the differential pressure ΔP (= Ps−Pc) between the suction pressure Ps (total pressure) and the crank chamber pressure Pc and the spring force of the spring 45. Moving.

Next, the operation of the compressor according to this embodiment will be described.
FIG. 4A shows a state of the valve body 44 during the maximum capacity operation in which the inclination angle of the swash plate 22 is maximized. During the maximum capacity operation, the crank chamber pressure Pc is decreased to be approximately equal to the static pressure Ps1, but the dynamic pressure Ps1 is increased, and the valve body 44 is pressed with the pressing force based on the dynamic pressure Ps1, and the valve body 44 is moved to the second valve chamber 47. The urging force of the spring 45 urging to the side acts, and the valve body 44 moves greatly downward on the second valve chamber 47 side and comes into contact with a protrusion provided at the bottom of the valve chamber 42.
At this time, the opening 50a of the oil passage 50 that opens into the valve chamber 42 is fully opened because the upper end surface of the valve body 44 is located below. As a result, the lubricating oil stored in the oil storage chamber 37 is introduced into the first valve chamber 46 through the oil passage 50, and as shown by the arrows in FIG. Then, the air is supplied to the suction chamber 32 through the suction passage 38 and the suction port 40. The lubricating oil supplied to the suction chamber 32 flows into the cylinder bore 12a together with the refrigerant gas and is used for lubricating the piston sliding portion.

Next, FIG. 4B shows a state of the valve body 44 during the minimum capacity operation in which the inclination angle of the swash plate 22 is minimized. During the minimum capacity operation, the crank chamber pressure Pc is substantially equal to the static pressure Ps1 of the suction pressure, and the dynamic pressure Ps1 hardly acts because the refrigerant is hardly sucked. Therefore, the valve body 44 is moved to an intermediate position of the valve chamber 42 by the biasing force of the spring 45, the opening 50a of the oil passage 50 is closed by the valve body 44, and the opening 50a of the oil passage 50 is fully closed. .
As a result, the lubricating oil stored in the oil storage chamber 37 is not supplied to the suction chamber 32 through the oil passage 50, and the amount of lubricating oil stored in the oil storage chamber 37 is increased to prevent the lubricating oil from being depleted.

Next, FIG. 4C shows the state of the valve body 44 during variable displacement operation when the inclination angle of the swash plate 22 is between the maximum and minimum. During variable displacement operation, the crank chamber pressure Pc becomes higher than the suction pressure Ps (total pressure), so that the valve body 44 has a biasing force of the spring 45 that biases the valve body 44 toward the second valve chamber 47. The pressing force based on the differential pressure ΔP that presses the valve body 44 toward the first valve chamber 46 acts preferentially, and the valve body 44 moves greatly toward the first valve chamber 46 side and comes into contact with the lower end portion of the partition wall 41. .
At this time, the opening 50 a of the oil passage 50 that opens into the valve chamber 42 communicates with the outer peripheral groove 51 formed in the valve body 44 and communicates with the first valve chamber 46 through the through hole 52. As a result, the lubricating oil stored in the oil storage chamber 37 is introduced into the first valve chamber 46 via the oil passage 50, the outer peripheral groove 51, and the through hole 52, as indicated by arrows in FIG. The suction chamber 32 is supplied through the first valve chamber 46, the hole 43, the suction passage 38 and the suction port 40.

By the way, the passage sectional area S2 of the through hole 52 is formed to be smaller than the passage sectional area S1 of the oil passage 50 (S1> S2), whereby the supply amount of the lubricating oil is reduced by the through hole 52. Accordingly, since an appropriate amount of lubricating oil squeezed by the through hole 52 can be supplied to the suction chamber 32, it is possible to prevent exhaustion of the lubricating oil in the oil storage chamber 37 while lubricating the piston sliding portion.
Thus, at the maximum capacity operation in which the piston 28 slides greatly, the opening amount of the oil passage 50 is maximized to increase the supply amount of the lubricating oil from the oil storage chamber 37, and the minimum capacity at which the piston 28 hardly slides. During operation, the opening of the oil passage 50 is minimized so that lubricating oil is not supplied from the oil storage chamber 37, and during variable displacement operation in which the piston 28 slides at an intermediate size according to the capacity, The opening of the passage 50 is narrowed to supply an appropriate amount of lubricating oil to the suction chamber 32.

The compressor 10 according to this embodiment has the following effects.
(1) The suction pressure Ps (total pressure) = static pressure Ps1 + dynamic pressure Ps2 acts on the upper surface of the first valve chamber 46 and the crank chamber pressure Pc acts on the lower surface of the second valve chamber. Further, the valve body 44 is urged toward the second valve chamber 47 by the spring 45. Accordingly, the valve body 44 moves up and down in the valve chamber 42 in accordance with the balance between the differential pressure ΔP (= Ps−Pc) between the suction pressure Ps (total pressure) and the crank chamber pressure Pc and the spring force of the spring 45. Moving. During the maximum capacity operation, the valve body 44 moves greatly downward on the second valve chamber 47 side, contacts the bottom of the valve chamber 42, and the opening 50a of the oil passage 50 is fully opened. Thus, the lubricating oil stored in the oil storage chamber 37 is supplied to the suction chamber 32 through the oil passage 50, the first valve chamber 46, the hole 43, the suction passage 38 and the suction port 40. The lubricating oil supplied to the suction chamber 32 flows into the cylinder bore 12a together with the refrigerant gas and can sufficiently lubricate the piston sliding portion. During the minimum capacity operation, the valve body 44 moves to an intermediate position of the valve chamber 42, the opening 50a of the oil passage 50 is closed by the valve body 44, and the opening 50a of the oil passage 50 is fully closed. As a result, the lubricating oil stored in the oil storage chamber 37 is not supplied to the suction chamber 32 through the oil passage 50, and the amount of lubricating oil stored in the oil storage chamber 37 is increased to prevent the lubricating oil from being depleted. During variable displacement operation, the valve body 44 moves greatly toward the first valve chamber 46 and comes into contact with the lower end of the partition wall 41. Accordingly, the opening 50 a of the oil passage 50 communicates with the outer peripheral groove 51 formed in the valve body 44 and communicates with the first valve chamber 46 through the through hole 52. Therefore, the lubricating oil stored in the oil storage chamber 37 is supplied to the suction chamber 32 through the oil passage 50, the outer peripheral groove 51 and the through hole 52, the first valve chamber 46, the hole 43, the suction passage 38 and the suction port 40. The By the way, since the passage cross-sectional area S2 of the through hole 52 is formed smaller than the passage cross-sectional area S1 of the oil passage 50, the supply amount of the lubricating oil is reduced by the through hole 52, and an appropriate amount of the lubricating oil is reduced. Can be supplied to the suction chamber 32, so that the lubricating oil in the oil storage chamber 37 can be prevented while lubricating the piston sliding portion.
(2) At the maximum capacity operation in which the piston 28 slides greatly, the opening amount of the oil passage 50 is maximized to increase the supply amount of the lubricating oil from the oil storage chamber 37, and the minimum capacity operation in which the piston 28 hardly slides. Sometimes, the opening of the oil passage 50 is minimized so that no lubricating oil is supplied from the oil storage chamber 37, and during variable displacement operation in which the piston 28 slides at an intermediate size according to the capacity, the oil passage The opening of 50 is narrowed down so that an appropriate amount of lubricating oil is supplied to the suction chamber 32. Therefore, it is possible to supply an appropriate amount of lubricating oil according to the discharge flow rate of the refrigerant, that is, the operating state, it is possible to prevent exhaustion of the lubricating oil in the oil storage chamber 37, and to improve the durability of the compressor 10. Improvements can be made.
(3) Since the communication passage 53 is formed by the outer peripheral groove 51 formed on the outer peripheral surface of the valve body 44 over the entire periphery, and the through hole 52 that allows the outer peripheral groove 51 to communicate with the first valve chamber 46. Even if the valve body 44 rotates in the circumferential direction in the valve chamber 42, the oil passage 50 and the outer circumferential groove 51 remain in communication with each other, and the lubricating oil is supplied from the oil passage 50 to the through hole 52 through the outer circumferential groove 51. Can be reliably guided.

(Second Embodiment)
Next, the compressor which concerns on 2nd Embodiment is demonstrated based on FIGS.
The compressor of this embodiment is obtained by changing the structure of the communication passage 53 formed in the valve body 44 in the first embodiment, and the other configurations are common.
Therefore, here, for convenience of explanation, a part of the reference numerals used in the previous explanation is used in common, the explanation of the common configuration is omitted, and only the changed part is explained.

As shown in FIGS. 5 and 6, the valve body 60 is formed with a notch 61 that opens on the second valve chamber 47 side on the outer peripheral surface of the valve body 60. The notch 61 is formed by forming a notch having a D-shaped cross section on the outer peripheral surface of the valve body 60. A communication passage 62 that opens to the second valve chamber 47 side is formed by the inner wall surface of the valve chamber 42 on which the valve body 60 slides and the notch 61.
Here, the passage cross-sectional area of the communication passage 62 corresponds to the area of the region between the cut surface of the notch 61 and the sliding surface 54 in FIG. 6. If this passage cross-sectional area is S3, then S3 < It is set to be S1 (however, the passage sectional area of the oil passage 50 is S1).

Next, the operation of the compressor according to this embodiment will be described with reference to FIG. The operation at the maximum capacity operation shown in FIG. 7 (a) and the operation at the minimum capacity operation shown in FIG. 7 (b) is the same as the operation in FIG. 4 (a) and FIG. 4 (b) in the first embodiment. Since they are basically the same, the description thereof is omitted.
In the variable displacement operation shown in FIG. 7C, the crank chamber pressure Pc becomes higher than the suction pressure Ps (total pressure), and the valve body 60 has a spring that biases the valve body 60 toward the second valve chamber 47. The pressing force based on the differential pressure ΔP that presses the valve body 60 toward the first valve chamber 46 acts more preferentially than the biasing force 45, and the valve body 60 moves largely toward the first valve chamber 46 and moves to the partition wall. 41 abuts the lower end of 41.

At this time, the opening 50 a of the oil passage 50 that opens into the valve chamber 42 is connected to a notch 61 formed in the valve body 60, and the oil passage 50 is connected via a communication passage 62 formed by the notch 61. Is communicated with the second valve chamber 47. As a result, as indicated by an arrow in FIG. 7C, the lubricating oil stored in the oil storage chamber 37 is introduced into the second valve chamber 47 via the oil passage 50 and the communication passage 62, and the second valve It is supplied to the crank chamber 16 through a passage 49 that connects the chamber 47 and the crank chamber 16.
By the way, the passage cross-sectional area S3 of the communication passage 62 is formed to be smaller than the passage cross-sectional area S1 of the oil passage 50 (S3 <S1). Accordingly, since an appropriate amount of lubricating oil squeezed by the communication passage 62 can be supplied to the crank chamber 16, it is possible to prevent exhaustion of the lubricating oil in the oil storage chamber 37 while lubricating the sliding portion in the crank chamber 16. .

As described above, in the second embodiment, during variable displacement operation, the sliding portion of the compressor is lubricated by supplying an appropriate amount of lubricating oil narrowed down by the communication passage 62 to the crank chamber 16. In the maximum capacity operation, the opening amount of the oil passage 50 is maximized to increase the supply amount of lubricating oil supplied from the oil storage chamber 37 through the oil passage 50 to the suction chamber 32, and the piston sliding portion Lubrication can be performed. Further, during the minimum capacity operation, the opening degree of the oil passage 50 is minimized so that the lubricating oil is not supplied from the oil storage chamber 37 through the oil passage 50 to the suction chamber 32 or the crank chamber 16.
Therefore, since it is possible to switch and set so that the lubricating oil is supplied to the suction chamber 32 and the crank chamber 16 according to the operating state, the sliding portion of the compressor can be lubricated widely, and the compressor Further improvement in durability can be achieved.

(Third embodiment)
Next, the compressor which concerns on 3rd Embodiment is demonstrated based on FIG.
The compressor of this embodiment is obtained by changing the formation position of the communication passage 53 formed in the valve body 60 in the second embodiment, and other configurations are common.
Therefore, here, for convenience of explanation, a part of the reference numerals used in the previous explanation is used in common, the explanation of the common configuration is omitted, and only the changed part is explained.

As shown in FIG. 8, a notch 71 that communicates with the opening 50 a of the oil passage 50 and extends downward is formed on the sliding surface 54 with the valve body 70 in the valve chamber 42. The notch 71 is formed in a groove shape and opens to the second valve chamber 47 side during variable displacement operation.
At the maximum capacity operation, as shown by a two-dot chain line in FIG. 8, the upper end surface of the valve body 70 is located below the opening 50a of the oil passage 50, and the position where the notch 71 and the valve body 70 slightly overlap each other. However, the lubricating oil is introduced into the first valve chamber 46 through the opening 50 a of the oil passage 50 and the notch 71.
During the minimum capacity operation, although not shown, the valve body 70 moves to a position overlapping the opening 50a and the notch 71 of the oil passage 50, and the opening 50a and the notch 71 of the oil passage 50 are closed by the valve body 70, Lubricating oil supply stops.

During variable displacement operation, as shown by the solid line in FIG. 8, the valve body 70 moves greatly to the first valve chamber 46 side and comes into contact with the lower end portion of the partition wall 41. At this time, the lower end portion of the valve body 70 is positioned slightly above the lower end portion of the notch 71, so that a passage hole 73 that opens to the second valve chamber 47 side is formed in the lower end portion of the notch 71. . The passage hole 73 forms a communication passage 72 that allows the oil passage 50 and the second valve chamber 47 to communicate with each other.
By the way, in this embodiment, the passage cross-sectional area of the communication passage 72 is formed between the lower end portion of the notch 71 and the lower end portion of the valve body 70, and the passage hole 73 that opens to the second valve chamber 47 side is formed. Although it is set so as to be determined by the size (opening area), the size of the passage hole 73 is smaller than the passage cross-sectional area S1 of the oil passage 50, so that lubricating oil is supplied by the communication passage 72. The amount is reduced.
In addition, the passage sectional area of the communication passage 72 formed between the notch 71 and the outer peripheral surface of the valve body 70 is formed to be smaller than the passage sectional area S1 of the oil passage 50, and the passage opens to the second valve chamber 47 side. The size of the hole 73 may be larger than the passage cross-sectional area S1.

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 first embodiment, it has been described that the communication passage 53 is formed by the outer peripheral groove 51 and the through hole 52. However, a plurality of the through holes 52 may be provided in the circumferential direction. A notch that connects the outer peripheral groove 51 and the first valve chamber 46 may be formed on the outer peripheral surface of the valve body 44. Further, the communication passage 53 may be formed only by the through hole 52.
In the second embodiment, it has been described that the communication passage 62 is formed by the notch 61, but instead of the notch 61, an outer peripheral groove formed in the valve body, the outer peripheral groove and the second valve chamber 47 The communication passage 62 may be formed by a hole connecting the two.
In each of the above embodiments, the communication passage has been described as a combination of an outer peripheral groove, a through hole, and a notch, or a single use. However, a valve body and a valve chamber can be provided without providing an outer peripheral groove, a through hole, and a notch. A communication passage may be formed by utilizing the clearance between the inner wall surface and the lubricating oil may be supplied to the suction chamber 32 or the crank chamber 16.

It is a longitudinal section showing the whole compressor composition concerning a 1st embodiment. It is an expanded sectional view of the principal part of the compressor concerning a 1st embodiment. It is the sectional view on the AA line of FIG. It is a mimetic diagram for explanation of operation of the compressor concerning a 1st embodiment. (A) Indicates the maximum capacity operation. (B) Indicates the minimum capacity operation. (C) The variable capacity operation is shown. It is an expanded sectional view of the principal part of the compressor concerning a 2nd embodiment. FIG. 6 is a sectional view taken along line B-B in FIG. 5. It is a mimetic diagram for explanation of operation of the compressor concerning a 2nd embodiment. (A) Indicates the maximum capacity operation. (B) Indicates the minimum capacity operation. (C) The variable capacity operation is shown. It is an expanded sectional view of the principal part of the compressor concerning a 3rd embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Compressor 11 Housing 16 Crank chamber 32 Suction chamber 37 Oil storage chamber 38 Suction passage 42 Valve chamber 44 Valve body 45 Spring (biasing member)
46 1st valve chamber 47 2nd valve chamber 48 1st channel | path 49 2nd channel | path 50 Oil channel | path 50a The opening part 53 of an oil channel | path (it consists of a "51 outer periphery groove | channel" and a "52 through-hole")
54 Sliding surface Ps Suction pressure Pc Crank chamber pressure S1 Cross-sectional area of oil passage S2 Cross-sectional area of communication passage

Claims (4)

A variable storage system is provided with an oil storage chamber for storing lubricating oil separated from the discharge gas in the compressor housing, and valve means for controlling the opening of an oil passage for guiding the lubricating oil stored in the oil storage chamber into the compressor. In the capacity type swash plate compressor,
The valve means includes a valve chamber provided in communication with a suction passage for introducing a refrigerant into the suction chamber and a crank chamber, a valve body provided slidably in the valve chamber, and the valve body. An urging member for energizing,
The valve chamber is divided into a first valve chamber in which a static pressure and a dynamic pressure of a refrigerant flowing through the suction passage are introduced by the valve body, and a second valve chamber in communication with the crank chamber. Partitioned,
The biasing member is disposed in the valve chamber, and biases the valve body toward the second valve chamber;
An opening portion of the oil passage that connects the valve chamber and the oil storage chamber is provided on a sliding surface with the valve body in the valve chamber, and the oil passage and the sliding surface are provided on the valve body or the sliding surface. A communication passage communicating with the first valve chamber or the second valve chamber is provided;
When the valve body slides in the valve chamber based on the respective pressure differences received from the first valve chamber and the second valve chamber, the opening of the oil passage becomes the maximum state during the maximum capacity operation, and the minimum capacity During operation, the opening of the oil passage is in a minimum state, and during variable displacement operation, the oil passage and the first valve chamber or the second valve chamber have a passage cross-sectional area smaller than that of the oil passage. A variable displacement swash plate compressor, wherein the opening of the oil passage is controlled so as to communicate with each other through the passage. 2. The communication passage is formed by an outer peripheral groove formed over the entire outer peripheral surface of the valve body and a through hole that communicates the outer peripheral groove with the first valve chamber. The variable capacity swash plate compressor described in 1. 2. The variable capacity swash plate compressor according to claim 1, wherein the communication passage is a notch formed on an outer peripheral surface of the valve body and opening toward the second valve chamber. 2. The notch according to claim 1, wherein the communication passage is formed on the sliding surface so as to communicate with the opening of the oil passage and is open to the second valve chamber side during variable displacement operation. Variable capacity swash plate compressor.

Images