JP2009079538A - Variable displacement gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress the manufacturing cost for a variable displacement gas compressor and to improve the flexibility in layout design of its oil supply passage and the like. <P>SOLUTION: As an oil supply passage upstream section 47a supplying refrigerator oil R to a displacement control valve 90 also serves as a part of an oil passage 23 formed in a rear side block 20 and an oil passage 46 formed in a cylinder 40, the need for forming the part of the oil passage 23 and the oil passage 46 separately from the oil supply passage upstream section 47a is eliminated, thereby suppressing the manufacturing cost and improving the layout design flexibility of the oil supply passage 47. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a variable capacity gas compressor, and more particularly, to an improvement in an oil passage for supplying high-pressure oil.

  Conventionally, a gas compressor (compressor) for compressing a gas such as a refrigerant gas and circulating the gas through the air conditioning system is used in an air conditioning system (hereinafter referred to as an air conditioning system).

  The gas compressor is provided with a compression chamber whose volume changes periodically. Gas is sucked into the compression chamber in a process of increasing the volume of the compression chamber, and gas is compressed in a process of decreasing the volume. The compressed gas is discharged outside the compression chamber.

  Here, for example, a vane rotary type compressor is known as one of general compressors.

  This vane rotary type compressor has a substantially cylindrical case with one open end and a front head connected to one end surface of the case so as to close the open one end opening of the case. The compressor main body is accommodated.

  The compressor main body is a cylindrical rotor that rotates integrally with the rotation shaft, a cylinder that surrounds the outer peripheral surface of the rotor, a cylinder having an inner peripheral surface with a substantially elliptical cross-sectional contour, and projects from the outer peripheral surface of the rotor, A plurality of plate-like vanes provided on the rotor at equal angular intervals around the rotation axis, the rotor and the cylinder, which can be moved forward and backward so as to maintain the protruding tip in contact with the inner peripheral surface of the cylinder The two side blocks (front side block and rear side block) arranged so as to sandwich the rotor and cylinder from the both end face sides, respectively, and the two side blocks and rotor according to the rotation of the rotating shaft The volume of the plurality of compression chambers defined by the two vanes that follow each other in the rotational direction of the cylinder and the rotor repeats increasing and decreasing, respectively. Inhaled gas chamber (e.g., refrigerant gas) to compress, and is configured to discharge to the outside of the compressor body.

  Here, the force that causes the vane to protrude toward the inner peripheral surface of the cylinder is due to the hydraulic pressure, and this hydraulic pressure is formed in the rotor through an oil passage formed in communication with the two side blocks and the cylinder. Acting on the vane back pressure chamber, the hydraulic pressure acting on the vane back pressure chamber urges the vane tip to abut against the inner circumferential surface of the cylinder.

  In addition, some of these gas compressors can change the discharge amount when the compressed gas is discharged to the outside.

  For example, a variable displacement compressor having the above-described vane rotary type compressor main body includes a front side block portion of the constituent members defining a compression chamber corresponding to the refrigerant gas compression stroke. A bypass passage is formed to connect the corresponding compression chamber and a space relatively lower in pressure than the pressure in the compression chamber (for example, a suction chamber into which the refrigerant gas is introduced), and pressures acting on both end faces thereof. A bypass valve is provided that switches between a state allowing the passage of the bypass passage (open state) and a state blocking (closed state) by displacing in the axial direction according to the difference between the two.

  When the bypass passage is open, a part of the refrigerant gas in the compression chamber is released to the low-pressure space through the bypass passage to reduce the amount of refrigerant gas discharged from the compression chamber, while the bypass passage is closed. In this case, since the refrigerant gas in the compression chamber is not released into the low-pressure space, the amount of refrigerant gas discharged from the compression chamber is maintained at the maximum state.

  Here, the pressure in the compression chamber acts on one end face of the both end faces of the bypass valve, and the high pressure oil pressure acts on the other end face, and this high pressure oil pressure is supplied to the bypass valve. What is present is a bypass check valve disposed in the front side block.

  The bypass check valve passes high pressure oil through the oil supply passage formed by communicating the rear side block, the cylinder and the front side block as a passage different from the oil passage communicating with the vane back pressure chamber. However, when a separately provided solenoid valve releases the oil pressure in the oil supply passage between the bypass check valve and the bypass valve, the bypass check valve Since the oil supply passage is closed, the hydraulic pressure supply to the downstream side of the bypass check valve is stopped.As a result, the bypass valve is displaced by the pressure in the compression chamber to open the bypass passage, and the refrigerant gas in the compression chamber is discharged. A part is released to the low-pressure space, and the amount of refrigerant gas discharged from the compression chamber is reduced.

When the solenoid valve stops releasing the oil pressure in the oil supply passage between the bypass check valve and the bypass valve, the high-pressure oil that permeates through a slight gap between the bypass check valve and the oil supply passage When the high pressure oil fills the oil supply passage on the downstream side of the bypass check valve, the pressure on the upstream and downstream sides of the bypass check valve is balanced and the bypass check valve As a result, the oil supply passage communicates with the bypass valve, high pressure oil is supplied to the other end face of the bypass valve, and the pressure of the oil acting on the other end face exceeds the pressure of the compression chamber. The bypass valve closes the bypass passage, and the amount of refrigerant gas discharged can be maximized (Patent Document 1).
JP 2006-037795 A

  By the way, in the variable capacity type gas compressor as described above, two oil paths are formed separately for the rear side block and the cylinder, that is, an oil supply path for variable capacity and an oil path for supplying hydraulic pressure to the vane back pressure chamber. In contrast to the fixed capacity gas compressor in which only the oil passage for supplying hydraulic pressure to the vane back pressure chamber is formed, the manufacturing cost increases due to a large number of processing steps for further forming the oil supply passage. However, there is a problem that the degree of freedom in the arrangement design of the oil passage and the oil supply passage itself and the degree of freedom in the arrangement design of other passages and fastening portions are impaired.

  The present invention has been made in view of the above circumstances, and is capable of reducing the manufacturing cost and improving the degree of freedom in arrangement design of the oil supply passage itself and other components of the gas compressor. The purpose is to provide a machine.

  In the variable capacity gas compressor according to the present invention, a part of an oil passage for supplying lubricating oil or hydraulic oil to the compression chamber from the outside of the compressor body is shared with a part of the oil supply passage leading to the capacity control valve. Therefore, it is not necessary to form a part of the oil passage separately from the oil supply passage, which reduces the manufacturing cost and the layout design of the oil supply passage itself and other components of the gas compressor. It improves the degree of freedom.

  That is, the capacity variable type gas compressor according to the present invention includes a compressor body in which a compression chamber for compressing gas is formed, and the compressor body includes a compression chamber corresponding to a compression stroke and a predetermined low pressure space. In a variable capacity gas compressor in which a bypass passage to be communicated and a displacement control valve for opening and closing the bypass passage are provided, and an oil supply passage for supplying hydraulic pressure to the displacement control valve from the outside of the compressor body is formed. A part of the oil supply passage is formed by sharing a part of an oil passage for supplying the hydraulic pressure to the compression chamber from the outside of the compressor body.

  According to the capacity variable type gas compressor according to the present invention configured as described above, a part of the oil passage for supplying the lubricating oil or the working oil from the outside of the compressor body to the inside of the compression chamber is a capacity control valve. Since the oil supply passage is formed so as to be shared with a part of the oil supply passage, it is not necessary to form a part of the oil passage separately from the oil supply passage, thereby reducing the manufacturing cost.

  Further, conventionally, since the oil passage and the oil supply passage are formed separately, both of these passages occupy each existing portion (formation region), but the variable capacity type according to the present invention In the gas compressor, only the existence part (formation region) of only the oil supply passage is occupied for the common part. Other components and members can be arranged or formed in the occupied portion corresponding to the section, and the degree of freedom in designing the arrangement of the oil supply passage itself and other components of the gas compressor can be improved.

  According to the variable capacity gas compressor according to the present invention, the manufacturing cost can be reduced, and the degree of freedom in the arrangement design of the oil supply passage itself and other components of the gas compressor can be improved.

  DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the best embodiment according to the capacity variable type gas compressor of the present invention will be described with reference to the drawings.

  FIG. 1 is a longitudinal sectional view showing a vane rotary compressor 100 which is an embodiment of a capacity variable type gas compressor according to the present invention.

  The illustrated compressor 100 is configured, for example, as a part of an air conditioning system (hereinafter simply referred to as an air conditioning system) that performs cooling using the heat of vaporization of a cooling medium, and condensing that is another component of the air conditioning system. Along with a condenser, an expansion valve, an evaporator, and the like (all not shown), they are provided on a cooling medium circulation path.

  The compressor 100 compresses the refrigerant gas G (gas) as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas G (compressed gas) to the condenser of the air conditioning system. To do. The condenser liquefies the compressed refrigerant gas G and sends it to the expansion valve as a high-pressure liquid refrigerant.

  The high-pressure liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange with the heat of vaporization.

  The compressor 100 includes an interior of a housing 10 including a substantially cylindrical case 11 having one end opened and a front head 12 connected to one end surface of the case 11 so as to close the one end opening of the case 11. The compressor body 60 that compresses the refrigerant gas G by rotating the rotating shaft 51, and the refrigerating machine oil R from the high-pressure refrigerant gas G that is assembled to the compressor body 60 and discharged from the compressor body 60. A configuration including a cyclone block 70 that separates (oil, lubricating oil, hydraulic oil) and a driving force transmission unit 80 that transmits a rotational driving force to be transmitted to the rotating shaft 51 of the compressor body 60 to the rotating shaft 51. is there.

  The compressor main body 60 accommodated in the housing 10 includes a rotating shaft 51 that is driven to rotate about an axis, a columnar rotor 50 that rotates integrally with the rotating shaft 51, and an outer peripheral surface of the rotor 50. And a cylinder 40 having a substantially elliptical inner peripheral surface 49 that surrounds the inner periphery of the cylinder 40 and a back pressure so as to protrude outwardly from the outer periphery of the rotor 50, and the tip of the protruding side is the inner peripheral surface of the cylinder 40. 49. The five plate-like vanes 58 embedded in the rotor 50 at equal angular intervals around the rotation shaft 51, and the rotor 50 can be moved back and forth so as to maintain the state in contact with the rotor 49. And a front side block 30 and a rear side block 20 fixed to the cylinder 40 so as to cover the end surfaces from the outside of both end surfaces of the cylinder 40, respectively.

  The volume of each compression chamber 48 defined by the two side blocks 20, 30, the rotor 50, the cylinder 40, and the two vanes 58, 58 that precede and follow the rotation direction of the rotation shaft 51 is By repeating the increase / decrease according to the rotation of the rotor 50, the refrigerant gas G sucked into each compression chamber 48 is compressed and discharged.

  One of the portions of the rotating shaft 51 protruding from both end faces of the rotor 50 is pivotally supported by the bearing portion 32 of the front side block 30 and extends outward through the front head 12. .

  Similarly, the other side of the protruding portion of the rotating shaft 51 is pivotally supported by the bearing portion 22 of the rear side block 20.

  The case 11 has a substantially cylindrical shape with one end closed, and houses the compressor body 60 from the side of the cyclone block 70 fixed to the rear side block 20.

  The front head 12 is assembled so as to cover the opened portion of the case 11, thereby forming an accommodation space inside the housing 10.

  The driving force transmission unit 80 is coupled to the pulley 82 rotatably supported on the outside of the boss of the front head 12 via the radial ball bearing 14, and the outer ring side is coupled to the side wall 82 a of the pulley 82 so as to rotate integrally with the pulley 82. The inner ring side is coupled to the rotation shaft 51 and rotates together with the rotation shaft. The inner ring side and the outer ring side are provided with a transmission plate 83 with a buffer material in which the inner ring side and the outer ring side are coupled by an elastic buffer member 83a. The compressor 100 is driven by the rotation driving force being transmitted to the rotating shaft 51 via the transmission plate 83 with a buffer material.

  The front head 12 is formed with a suction port 12a through which a low-pressure refrigerant gas G is sucked from the evaporator. A check valve 12b for preventing the refrigerant gas G from flowing backward is provided in the suction port 12a. Yes.

  The suction port 12a communicates with a suction chamber 34 formed between the front side block 30 and the front head 12 of the compressor body 60 accommodated in the housing 10, and the refrigerant gas G 34 is sucked into the compression chamber 48 of the compressor main body 60 through the suction hole 31.

  On the other hand, the case 11 is formed with a discharge port 11a for discharging the high-pressure refrigerant gas G compressed by the compressor body 60 to the condenser.

  The discharge port 11 a communicates with the discharge chamber 21 defined by the rear side block 20 and the case 11 of the compressor main body 60 accommodated in the housing 10, and the refrigerant gas G is supplied to the compressor main body 60. The gas is discharged from the compression chamber 48 to the discharge chamber 21 through the cyclone block 70.

  As shown in FIG. 2 by arrow A in FIG. 1, the cyclone block 70 is assembled and fixed to the outer surface of the rear side block 20 in the compressor main body 60 by a fastening member such as a bolt.

  When the high-pressure refrigerant gas G discharged from the compression chamber 48 and mixed with the refrigerating machine oil R passes through the filter provided in the cyclone block 70, the refrigerant gas G passes through the filter, and the case 11 and the compressor It flows into the discharge chamber 21 defined by the main body 60, and is sent to the condenser through the discharge port 11a.

  On the other hand, the refrigerating machine oil R is separated from the refrigerant gas G because it is aggregated by the filter. When the amount of aggregation increases, the refrigerating machine oil R drops downward due to its own weight and is stored at the bottom of the discharge chamber 21.

  Here, the compressor main body 60 of the compressor 100 is supplied with the oil pressure of the refrigerating machine oil R stored in the bottom of the discharge chamber 21 into the compressor main body 60, and is a vane that is a sliding portion inside the compressor 60. An oil passage is formed for reducing friction generated between the rotor 58 and the rotor 50 and the side blocks 20 and 30 and the cylinder 40 and for causing a thrust force to act on the vane 58.

  This oil passage communicates with an oil passage 23 formed in the rear side block 20, an oil passage 46 formed in the cylinder 40 in communication with the oil passage 23 in the rear side block 20, and an oil passage 46 in the cylinder 40. The oil passage 33 is formed in the side block 30, and the oil passage 23 of the rear side block 20 reaches the bearing portion 22, and a slight gap between the circumferential surface of the rotating shaft 51 and the surface of the bearing portion 22 (throttling due to the gap). The pressure drops and the pressure drops), or through the oil passage 23 without passing through this gap, and the refrigerating machine oil inside the compression body 40 (between the rear side block 20 and the rotor 50). R is supplied.

  The oil passage 46 of the cylinder 40 has one end communicating with the oil passage 23 of the rear side block 20 and the other end communicating with the oil passage 33 of the front side block 30, and the oil passage 33 of the front side block 30 is One end thereof communicates with the oil passage 46 of the cylinder 40, the other end reaches the bearing portion 32 of the front side block 30, and the refrigerating machine oil supplied from the oil passage 23 of the rear side block 20 via the oil passage 46 of the cylinder 40. R passes through a slight gap between the peripheral surface of the rotating shaft 51 and the surface of the bearing portion 32 (a pressure loss is caused by the restriction caused by the gap and the pressure is reduced) or without passing through this gap. The oil is supplied to the inside of the compression main body 60 (between the front side block 30 and the rotor 50) through the oil passage 33.

  Here, the compressor 100 according to the present embodiment is a variable capacity compressor capable of changing the amount of the refrigerant gas G discharged from the compression chamber 48, and the refrigerant in the compression chamber 48 originally in the compression stroke. The amount of the refrigerant gas G trapped in the compression chamber 48 is reduced by releasing the gas G to the outside of the compression chamber 48 and delaying the timing at which the actual compression action is started. The amount is reduced.

  As shown in FIG. 3, such a capacity variable effect is achieved by the compression chamber 48 corresponding to the compression stroke and the suction chamber 34 (predetermined pressure lower than the pressure in the compression chamber 48). And the capacity control valve 90 for opening and closing the bypass path 36 and the refrigerating machine oil R accumulated in the bottom of the discharge chamber 21 (outside of the compressor body 60) are hydraulically applied to the capacity control valve 90. And the oil supply passage 47 for supplying the oil.

  Here, the capacity control valve 90 supplies a bypass valve 91 (bypass valve) that opens and closes the bypass passage 36 by hydraulic pressure and supplies the hydraulic pressure supplied through the oil supply passage 47 to the bypass valve 91 or bypasses the supply to stop. A check valve 92 (bypass check valve) and a solenoid valve 93 are provided. Here, the bypass valve 91 and the bypass check valve 92 are provided in the front side block 30, and the electromagnetic valve 93 is provided in the front head 12.

  One end of the bypass passage 36 opens toward the compression chamber 48 corresponding to the compression stroke, this opening serves as a bypass hole 48a, and the other end opens into the suction chamber 34.

  The bypass valve 91 is displaced in the axial direction in accordance with the difference in pressure acting on one end surface 91a facing the bypass hole 48a and the opposite end surface 91b, and allows passage of the bypass passage 36. A state (open state; see FIG. 3B) and a state where the bypass hole 48a is blocked by one end face 91a to block the passage of the bypass passage 36 (closed state; see FIG. 3A) are switched. .

  When the bypass passage 36 is in an open state, a part of the refrigerant gas G in the compression chamber 48 is released to the suction chamber 34 through the bypass passage 36, thereby reducing the amount of the refrigerant gas G discharged from the compression chamber 48. When the bypass passage 36 is in the closed state, the refrigerant gas G in the compression chamber 48 is not released to the suction chamber 48, so that the amount of the refrigerant gas G discharged from the compression chamber 48 is not reduced.

  The pressure acting on the other end face 91 b of the bypass valve 91 is controlled by the bypass check valve 92. That is, the other end surface 91b of the bypass valve 91 faces a portion of the oil supply passage 47 on the downstream side of the bypass check valve 92 (hereinafter referred to as an oil supply passage downstream portion 47b), as shown in FIG. In addition, in a state where the bypass check valve 92 opens the oil supply passage 47 (a state where the oil supply passage upstream portion 47a and the oil supply passage downstream portion 47b communicate with each other), the refrigeration supplied to the oil supply passage downstream portion 47b is performed. Since the pressure of the machine oil R is a pressure acting on the refrigerating machine oil R stored in the discharge chamber 21, it is higher than the pressure acting on the compression chamber 48 corresponding to the compression stroke. The passage 36 is kept closed, and the amount of the refrigerant gas G discharged from the compression chamber 48 is maximized.

  Here, the electromagnetic valve 93 opens and closes the oil supply passage downstream portion 47b so as to switch whether the refrigerating machine oil R flowing through the oil supply passage downstream portion 47b is allowed to escape to the suction chamber 34 or not. When the bypass passage 36 is closed (FIG. 3A), the solenoid valve 93 is set so that the refrigerating machine oil R flowing through the oil supply passage downstream portion 47b does not escape to the suction chamber 34.

  On the other hand, as shown in FIG. 3 (b), when the solenoid valve 93 is switched so as to release the refrigerating machine oil R flowing through the oil supply passage downstream portion 47b to the suction chamber 34, the bypass check valve 92 of the oil supply passage upstream. A pressure difference is generated between the end surface facing the portion 47a and the end surface facing the oil supply passage downstream portion 47b, and the bypass check valve 92 is located in the downstream portion of the oil supply passage where the pressure is relatively low against the biasing force of the illustrated spring. Displace to 47b side.

  When the bypass check valve 92 is displaced, the end face of the bypass check valve 92 facing the oil supply passage upstream portion 47a is in a state where the oil supply passage 47 is closed by itself (the oil supply passage upstream portion 47a and the oil supply passage downstream portion 47b communicate with each other). The pressure of the refrigerating machine oil R does not act on the oil supply passage downstream portion 47b. Therefore, the pressure acting on the other end surface 91b of the bypass valve is the pressure acting on the one end surface 91a (compression stroke). Therefore, the bypass valve 91 opens the bypass passage 36 as a result. Therefore, the amount of the refrigerant gas G discharged from the compression chamber 48 is reduced.

  Thereafter, when the solenoid valve 93 stops releasing the oil pressure in the oil supply passage downstream portion 47b between the bypass check valve 92 and the bypass valve 91, a slight gap between the bypass check valve 92 and the oil supply passage 47 is obtained. When the refrigeration oil R penetrating from the oil gradually begins to accumulate in the oil supply passage downstream portion 47b and the refrigeration oil R fills the oil supply passage downstream portion 47b, the pressure on the upstream side and the downstream side of the bypass check valve 92 is balanced. The bypass check valve 92 is displaced, and as a result, the oil supply passage upstream portion 47a and the oil supply passage downstream portion 47b communicate with each other, and the pressure of the refrigerating machine oil R is supplied to the other end surface 91b of the bypass valve 91. When the pressure of the refrigerating machine oil R acting on the other end surface 91b exceeds the pressure of the compression chamber 48, the bypass valve 91 closes the bypass passage 36, and the pressure The amount of the refrigerant gas G discharged from the chamber 48 can be returned to the maximum.

  Here, a part of the oil passage 23 formed in the rear side block 20 among the oil passages 23, 46, 33 for supplying the refrigerating machine oil R from the discharge chamber 21 outside the compressor main body 60 to the compression chamber 48. The oil passage 46 formed in the cylinder 40 is formed so as to share the oil supply passage upstream portion 47a (a part of the oil supply passage).

  That is, part of the oil passage 23 formed in the rear side block 20 and the oil passage 46 formed in the cylinder 40 are shared by the oil supply passage upstream portion 47a.

  As a result, part of the oil passage 23 that supplies the refrigerating machine oil R to the compression chamber 48 from the outside of the compressor body 60 and the oil passage 46 are part of the oil supply passage 47 that communicates with the capacity control valve 90. Since it is formed so as to be shared by the upstream portion 47a, it is not necessary to form a part of the oil passage 23 and the oil passage 46 separately from the oil supply passage upstream portion 47a, thereby suppressing the manufacturing cost. be able to.

  Further, conventionally, since a part of the oil passage 23 and the oil passage 46 and the oil supply passage upstream portion 47a are separately formed, these occupy each existing portion (formation region) separately. However, since the compressor 100 according to the present embodiment occupies only the portion (formation region) where only the oil supply passage 47 is occupied, the shared portion does not need to be separately formed. Another component or member can be arranged or formed in a part of the oil passage 23 and the occupied portion corresponding to the oil passage 46, and the freedom of arrangement design of the oil supply passage 47 itself and other components of the compressor 100 can be achieved. The degree can be improved.

  Further, in the compressor 100 of the present embodiment, a part of the oil passage 23 sharing a part of the oil supply passage 47 is formed in the rear side block 20, and the oil passage 46 communicates with the oil passage 23 and is connected to the cylinder 46. And an oil passage that supplies the refrigerating machine oil R from the outside of the compressor body 60 (discharge chamber 21) to the compression chamber 48 because it is a portion upstream of the bypass check valve 92 (oil supply passage upstream portion 47a). 23, 46, 33 can be prevented from fluctuating depending on the operating state of the bypass check valve 92 (opening / closing state of the oil supply passage 47), and the urging force that causes the compression chamber 21 (particularly the vane 58 to protrude). It is possible to avoid fluctuations in the hydraulic pressure applied to the vane back pressure chamber (not shown) in which the pressure is applied.

  That is, a part of the oil passages 23, 46, 33 for supplying the refrigerating machine oil R from the discharge chamber 21 to the compression chamber 48 is a part of the oil supply passage 47 on the downstream side of the bypass check valve 92 (oil supply passage downstream portion 47 b ), When the solenoid valve 93 is opened and the oil pressure in the oil supply passage downstream portion 47b is released to the suction chamber 34 (FIG. 3B), the oil supply passage downstream portion 47b In the oil supply passage upstream portion 47a, and the oil pressure in the oil passages 23, 46, and 33 also greatly decreases according to the oil pressure in the oil supply passage downstream portion 47b. 23, 46 and 33 cannot secure the original hydraulic pressure to be supplied to the compression chamber 21 (including the vane back pressure chamber).

  However, in the compressor 100 of the present embodiment, the oil passages 23, 46, and 33 are not shared with the oil supply passage downstream portion 47 b and depend on the internal pressure of the discharge chamber 21 regardless of the operating state of the bypass check valve 92. Therefore, the oil supply passage upstream portion 47a that maintains the high pressure is shared only with the oil supply passage upstream portion 47a, so that the supply hydraulic pressure to the compression chamber 21 (including the vane back pressure chamber) can be prevented from decreasing.

  Further, the compressor 100 according to the present embodiment is provided with a refrigeration at the inlet of the oil supply passage 47 in the compressor main body 60 for the purpose of preventing foreign matters mixed in the refrigerator oil R from affecting the operation of the capacity control valve 90. A filter 99 for filtering the machine oil R is provided.

  The foreign matter mixed in the refrigerating machine oil R is prevented from flowing into the oil supply passage 47 by the filter 99, thereby ensuring proper operation of the capacity control valve 90.

  Moreover, since the inlet portion of the oil passage 23 is also shared by the oil supply passage 47, the refrigeration oil R supplied to the oil passages 23, 46, and 33 is also the one in which foreign matters are removed by the filter 99 (see FIG. 2). ), It is possible to avoid the foreign matter from affecting the sliding portion inside the compressor main body 60 to which the refrigerating machine oil R is supplied.

  The compressor 100 of the above-described embodiment is a vane rotary type gas compressor, but the capacity variable type gas compressor according to the present invention is not limited to the vane rotary type of the embodiment. The present invention can also be applied to a gas compressor of a type, for example, a gas compressor of a swash plate reciprocating type or a scroll type.

It is a longitudinal section showing a vane rotary type compressor which is one embodiment of a gas compressor concerning the present invention. It is a figure which shows the compressor main body by the arrow A in FIG. It is a figure which shows the detail of the B section in FIG. 1, (a) is the state in which the capacity | capacitance control valve was closed (state in which discharge capacity was the maximum), (b) was the state in which the capacity control valve was opened (discharge capacity decreased) State).

Explanation of symbols

20 Rear side blocks 23 and 46 Oil passage 30 Front side block 40 Cylinder 47 Oil supply passage 47a Oil supply passage upstream portion 90 Capacity control valve 91 Bypass valve 92 Bypass check valve 93 Solenoid valve 100 Compressor (variable capacity type gas compressor)
G Refrigerant gas (gas)
R refrigerator oil (refrigerator oil)

Claims (3)

Comprising a compressor body formed with a compression chamber for compressing gas;
The compressor main body is provided with a bypass passage for communicating a compression chamber corresponding to a compression stroke and a predetermined low pressure space, and a capacity control valve for opening and closing the bypass passage, and the capacity control valve from the outside of the compressor main body. In the variable capacity type gas compressor in which an oil supply passage for supplying hydraulic pressure is formed,
A part of the oil supply passage is formed by sharing a part of an oil passage for supplying the hydraulic pressure to the compression chamber from the outside of the compressor body. The compressor body includes a rotor that rotates integrally with a rotation shaft, a cylinder that surrounds the outer peripheral surface of the rotor, an inner peripheral surface having a substantially elliptical cross-sectional outline, and projects from the outer peripheral surface of the rotor, A vane that can be moved forward and backward so as to maintain a state in which the protruding tip is in contact with the inner peripheral surface of the cylinder, and the rotor and the cylinder are sandwiched from both ends of the rotor and the cylinder, respectively. With two side blocks arranged in
The bypass passage is formed in one side block of the two side blocks,
The capacity control valve includes a bypass valve that opens and closes the bypass passage by hydraulic pressure, and a bypass check valve and an electromagnetic valve that switches supply / stop of the hydraulic pressure supplied through the oil supply passage to the bypass valve,
The oil supply passage is formed by communicating the other side block of the side blocks, the cylinder, and the one side block,
The portion of the oil passage sharing a part of the oil supply passage includes a portion formed in the other side block and the cylinder, and is a portion on the upstream side of the bypass check valve. The variable capacity gas compressor according to claim 1, wherein the variable capacity gas compressor is provided.   3. The variable capacity gas compression according to claim 2, wherein a filter that filters oil supplied to the oil supply passage is provided at an inlet of the oil supply passage in the compressor body. Machine.

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