JP2006022651A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce load acting on a fastening bolt fastening a support member retaining a delivery chamber and a compressor body while suppressing reduction of volume of an inside of the delivery chamber in a gas compressor. <P>SOLUTION: Opening area of a case 11 defined by an inner circumference edge part of a projecting part 11a is reduced by projecting one end to be an opening of the case 11 toward a center direction of a rotary shaft 51. Pressure receiving area facing the delivery chamber 16 (case side space) corresponding to opening area of the case 11 of a compressor body (a rotary shaft 51, a rotor 50, a cylinder and both side block 20, 30) attached on one end is reduced. Consequently, reduction of volume of the delivery chamber 16 is suppressed while load on a bolt 72 (fastening member) with a hexagon hole fastening a center plate 12 (support member) and a case 11 is reduced. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a gas compressor, and more particularly, to an improvement in a load acting between a support member that supports a compressor body and a case.

  Conventionally, air compressors for compressing refrigerant gas and circulating the refrigerant gas through the system have been used in air conditioning systems (hereinafter referred to as air conditioning systems).

  Here, as a gas compressor, a reciprocating type or a rotary type is put to practical use as an operation method, and a rotary type gas compressor shown in FIG. 7 is known, for example. The illustrated gas compressor is a vane rotary type compressor 100, and the main body of the compressor is driven by an electric motor 90 built in the housing 10.

  Specifically, an electric motor 90 is disposed therein, and a housing 10 including a motor housing 13 having one end opened in a direction in which the rotation shaft 91 of the electric motor 90 extends and a case 11 having one end opened. The compressor main body having a rotating shaft 51 that rotates integrally with the rotating shaft 91 of the electric motor 90 and one end of the case 11 are fastened so that the opening of the motor housing 13 and the opening of the case 11 face each other. The internal space of the housing 10 formed in a state where the both bolts 11 and 13 are fastened by the fastening bolt 71 is divided into a space on the motor housing 13 side and a space on the case 11 side, and is disposed in the space on the case 11 side. And a center plate 12 (supporting member) for holding the compressor body.

  Here, the center plate 12 is fastened and fixed to one end of the case 11 by fastening bolts 72.

  The compressor body includes a rotor 50 (rotary body) that rotates integrally with the rotation shaft 51 around the rotation shaft 51, and a cylinder 40 that has an elliptical cross-sectional outline on the inner peripheral surface that covers the outer periphery of the rotor 50. The front side block 20 and the rear side block 30 that sandwich the rotor 50 and the cylinder 40 from both end surface sides of the rotor 50 and the cylinder 40, respectively, and a plurality of vanes (not shown) that can project from the rotor 50 toward the inner peripheral surface of the cylinder 40. It is the structure provided with.

  As the rotor 50 rotates, the volume of the space (compression chamber) surrounded by the rotor 50, the cylinder 40, the two side blocks 20, 30 and the two vanes before and after the rotation direction changes periodically. The refrigerant gas G (gas) sucked into the compression chamber is compressed to a high pressure and discharged.

  Note that the rotating shaft 91 of the electric motor 90 and the rotating shaft 51 of the compressor body are physically separate members, and may be integrally formed.

  The motor housing 13 is formed with a suction port 14 for taking in the refrigerant gas G from the outside. The refrigerant gas G sucked from the suction port 14 is outside the space occupied by the electric motor 90 in the internal space on the motor housing 13 side. To the void space (suction chamber) 15.

  On the other hand, the case 11 is formed with a discharge port 17 for discharging the compressed refrigerant gas G to the outside, and the high-pressure refrigerant gas G discharged from the compressor body is in the space of the compressor body in the case 11 side. It is discharged from the discharge port 17 to the outside through a space (discharge chamber) 16 other than the occupied space.

  Then, the refrigerant gas G supplied to the suction chamber 15 is sucked into the compressor body through the vent hole 12 a formed in the center plate 12 and compressed to a high pressure, and discharged from the discharge port 17 through the discharge chamber 16. Is done.

  In FIG. 7, one end of the rotating shaft 91 of the electric motor 90 is pivotally supported on the motor housing 13 by a ball bearing 93. The rear side block 30 of the compressor body has an oil separator (not shown) that is a wire mesh for separating the refrigerating machine oil R mixed in the refrigerant gas G discharged from the compression chamber into the discharge chamber 16 from the refrigerant gas G. ) Equipped with a cyclone block 60.

  7 shows that the center plate 12 and the motor housing 13 are separate from each other. However, even if the center plate 12 and the motor housing 13 are integrated, the discharge chamber has a high pressure. There is no change (Patent Document 1).

The same applies to a gas compressor that does not include the electric motor 90.
JP 2004-36455 A

  By the way, since the high-pressure refrigerant gas G is discharged into the discharge chamber 16 of the compressor 100 described above, the internal pressure F of the discharge chamber 16 is high, and this internal pressure F acts on the center plate 12 via the compressor body, The fastening bolt 72 that fastens the center plate 12 and the case 11 acts as a tensile load.

  Similarly, when the center plate 12 and the motor housing 13 are integrally formed, a tensile load is applied to a fastening bolt (corresponding to the fastening bolt 71 in FIG. 7) that fastens the case 11 and the motor housing 13. In the case where the electric motor 90 is not provided, that is, the motor housing 13 is not provided, a fastening bolt (FIG. 7) for fastening the case 11 and the front head (corresponding to the center plate 12 in FIG. 7). The tensile load acts on the fastening bolt 72 in FIG.

  Here, in particular, when the refrigerant gas G is a high-pressure operating refrigerant gas such as carbon dioxide gas (R744) or R410a, the discharge pressure is significantly higher than that of a general freon gas or the like that is a traditional traditional refrigerant gas. For this reason, a tensile load stronger than that of a general gas compressor using Freon gas acts on the fastening bolt described above. Therefore, it has been difficult to reduce the number of fastening members for the purpose of weight reduction and manufacturing cost reduction.

  Therefore, it is conceivable to reduce the pressure acting on the compressor main body or the center plate 12 by reducing the discharge chamber 16 itself to reduce the pressure receiving area of the compressor main body or the center plate 12 facing the discharge chamber 16. However, if the discharge chamber 16 is made smaller, the flow rate of the refrigerant gas G discharged into the discharge chamber 16 cannot be reduced to a flow rate suitable for separating the refrigerating machine oil R, and the separating performance of the refrigerating machine oil R is lowered. As a result, the amount of the refrigerating machine oil R taken away from the compressor 100 increases, which may hinder lubrication and the like inside the compressor 100.

  The present invention has been made in view of the above circumstances, and provides a gas compressor capable of reducing a load acting on a fastening member that fastens a case and a support member while suppressing a reduction in the volume inside the discharge chamber. It is intended to provide.

  The gas compressor according to the present invention reduces the opening area of the case by projecting one end that becomes the opening of the case toward the center of the rotating shaft, and the compressor main body attached to the one end The pressure receiving area of the support member facing the case side space corresponding to the opening area of the case is reduced, and the load on the fastening bolt for fastening the support member and the case is reduced, and the volume of the case side space is reduced. Is suppressed.

  That is, the gas compressor according to claim 1 of the present invention includes a compressor body having a rotating shaft, a case having one end opened in a direction in which the rotating shaft extends, and the one end portion of the case. And a support member that holds the compressor body disposed in an internal space surrounded by the case, and discharges the gas compressed by the compressor body to the space inside the case. In the gas compressor, the one end portion of the case protrudes toward the center of the rotating shaft to reduce the opening area of the case.

  Like the case, the support member may function as a case with an outer shape that partitions the external space and the internal space, or the internal space surrounded by the case and the other case member, The member may be divided so as to be divided into two spaces.

  In addition, the structure in which one end portion of the case projects toward the center of the rotating shaft has a narrowed opening with respect to the inside of the case. Therefore, when molding the case with a mold, a sand mold is used. Is preferred. Of course, without using a sand mold, the inside of the case is molded by die casting, for example, so that the inside of the case is approximately the same as the narrowed opening, and then the inside of the case is subjected to processing such as cutting, so that the opening is open to the inside. It can also be molded as a relatively constricted one.

Here, since the high-pressure gas is discharged from the compressor body, the space inside the case becomes a high pressure. The internal pressure in the space on the case side can be instantaneously regarded as a substantially static pressure p [N / mm ² ]. Each member existing in the space has an area S [ A load F [N] (= pS) corresponding to mm ² ] acts.

  The load F along the rotation axis direction acting on the support member that supports the compressor main body is a load (F = pS) corresponding to the opening area S of the case. Of course, the support member does not block the entire opening of the case side, but the compressor body blocks the opening of the case side, whereby the surface of the compressor perpendicular to the rotation axis (total area ΣSi = S) A static pressure p acts on the compressor body, and a load F (= pS) acts on the compressor body. The load F acting on the compressor body acts on a support member that supports the compressor body.

  In this regard, the gas compressor according to the present invention acts on the support member because one end portion forming the opening of the case protrudes toward the center of the rotating shaft and the opening area of the case is reduced. The load is reduced.

  Therefore, the load acting on the fastening member that fastens the support member and the case can be reduced.

  Further, since only one end portion of the case is overhanging, the volume inside the case is not significantly reduced. As a result, it is possible to avoid the effect of suppressing the decrease in the flow rate of the discharge gas in the space inside the case, which occurs when the volume is significantly reduced.

  Here, in the gas compressor, lubricating oil (refrigerator oil or the like) is used for lubrication of an internal mechanism portion, and for obtaining a back pressure of the vane in other gas compressors such as a vane rotary type, A part of this lubricating oil is mixed with the gas to be compressed, discharged from the compressor body, and separated from the gas in the space on the case side. However, if the flow rate does not decrease, this oil separation performance is impaired. It is.

  In this regard, the gas compressor according to the present invention can prevent the oil separation performance from being impaired in order to avoid the effect of suppressing the decrease in the flow rate of the discharged gas in the space inside the case.

  According to a second aspect of the present invention, there is provided a gas compressor including a motor housing having one end opened in a direction in which a rotating shaft of an electric motor housed therein extends, a case having one end opened, and the electric motor. The compressor main body having a rotating shaft that rotates integrally with the rotating shaft of the motor and the one end portion of the case are fastened, and the opening of the motor housing and the opening of the case are opposed to each other. A space on the motor housing side is provided with a support member for partitioning an internal space into a space on the motor housing side and a space on the case side and holding the compressor body disposed in the space on the case side. In the gas compressor that is formed in the support member and sucked into the compressor main body through the ventilation hole and compressed, and the compressed gas is discharged into the case-side space. The one end of the serial case, protrudes toward the center of said rotary shaft, characterized in that by reducing the opening area of the case.

  In the configuration in which one end portion of the case projects toward the center of the rotating shaft, the opening is narrowed with respect to the inside of the case. Therefore, it is preferable to use a sand mold when molding the case with a mold. . Of course, without using a sand mold, the inside of the case is molded by die casting, for example, so that the inside of the case is approximately the same as the narrowed opening, and then the inside of the case is subjected to processing such as cutting, so that the opening is open to the inside. It can also be molded as a relatively constricted one.

  Here, since the high-pressure gas is discharged from the compressor main body, the case-side space has a high pressure. The internal pressure in the space on the case side can be regarded as a substantially static pressure instantaneously, and a load corresponding to the area exposed in the space acts on each member existing in the space.

  And the load along the rotation axis direction that acts on the support member that supports the compressor body is a load corresponding to the opening area of the case. Of course, the support member does not block the entire opening on the case side, but the compressor body blocks the opening on the case side, so that static pressure acts on the surface of the compressor perpendicular to the rotation axis. A load acts on the compressor body, and the load F acting on the compressor body acts on a support member that supports the compressor body.

  In this regard, the gas compressor according to the present invention acts on the support member because one end portion forming the opening of the case protrudes toward the center of the rotating shaft and the opening area of the case is reduced. The load is reduced.

  Therefore, the load acting on the fastening member that fastens the support member and the case can be reduced.

  Further, since only one end portion of the case is overhanging, the volume inside the case is not significantly reduced. As a result, it is possible to avoid the effect of suppressing the decrease in the flow rate of the discharge gas in the case-side space, which occurs when the volume is significantly reduced.

  Here, in the gas compressor, lubricating oil (refrigerator oil or the like) is used for lubrication of an internal mechanism portion, and for obtaining a back pressure of the vane in other gas compressors such as a vane rotary type, A part of this lubricating oil is mixed with the gas to be compressed, discharged from the compressor body, and separated from the gas in the space on the case side. However, if the flow rate does not decrease, this oil separation performance is impaired. It is.

  In this regard, the gas compressor according to the present invention can prevent the oil separation performance from being impaired in order to avoid the effect of suppressing the decrease in the flow rate of the discharged gas in the case-side space.

  A gas compressor according to claim 3 of the present invention is the gas compressor according to claim 1 or 2, wherein the gas is a high-pressure operating refrigerant gas.

  Here, as the high-pressure operating refrigerant gas, for example, a carbon dioxide gas (R744) or a refrigerant gas such as R410a can be applied.

  A gas compressor that compresses high-pressure refrigerant gas is compressed because the pressure of the gas discharged from the main body of the compressor is higher than that of conventional chlorofluorocarbon, which is a traditional refrigerant gas. The pressure in the space on the side of the case is much higher than that using such a general chlorofluorocarbon gas.

  For this reason, the load along the rotation axis direction acting on the support member becomes very strong, and the load reducing effect according to the present invention can be exhibited more remarkably. That is, in the gas compressor using the high-pressure operating refrigerant gas, since the load acting on the support member is very strong, it is necessary to increase the number of fastening members that fasten the support member and one end of the case. In the gas compressor according to the present invention, since the load acting on the support member can be reduced, there is no need to increase the number of fastening members that fasten the support member and one end of the case, or the increased number can be increased. Can be suppressed.

  Moreover, when the high-pressure operating refrigerant gas is used, there is a feature that the desired refrigeration capacity can be easily obtained even if the size (capacity) of the compressor body is reduced due to the characteristics of the gas. Therefore, when one end of the case is extended toward the center of the rotating shaft to reduce the opening area of the case, the desired discharge pressure is secured even if the size of the compressor body is reduced accordingly. Is possible.

  A gas compressor according to a fourth aspect of the present invention is the gas compressor according to any one of the first to third aspects, wherein the compressor body rotates integrally with the rotary shaft around the rotary shaft. A rotating body, a cylinder that covers the outside of the outer peripheral surface of the rotating body, two side blocks that sandwich the rotating body and the cylinder from both end surface sides of the rotating body, and the rotating body, A plurality of vanes that can project in the inner peripheral surface direction of the cylinder, and the support member covers a side block of the two side blocks on the side of the support member and the outside of the cylinder. Of the two side blocks, the outer peripheral edge of the side block on the case side is in contact with the inner peripheral edge of the opening of the case.

  The main body of the compressor rotates around the rotation axis integrally with the rotation shaft, the cylinder that covers the outer periphery of the rotation body, the rotation body and the cylinder from the both end surfaces of the rotation body and the cylinder, respectively. A so-called vane rotary type gas compressor is provided with two sandwiched side blocks and a plurality of vanes capable of projecting from the rotating body toward the inner peripheral surface of the cylinder. The suction chamber in which the gas sucked into the compressor body, that is, the gas to be sucked into the compression chamber, and the discharge chamber (the space on the case side) from which the high-pressure gas is discharged from the compression chamber, They are arranged on opposite sides of the compressor body.

  Since the suction chamber is at a low pressure and the discharge chamber is at a high pressure, the compressor main body has a structure that is essentially easily pressed from the discharge chamber side to the suction chamber side by the pressure balance between the chamber pressures.

  Therefore, the load applied to the support member is large. Therefore, the effect of reducing the load on the support member, which is exhibited by the gas compressor of the present invention, is more effectively exhibited.

  A gas compressor according to claim 5 of the present invention is the gas compressor according to claim 4, wherein a passage for lubricating oil is formed in the side block on the side of the case, and an oil supply port of the passage for lubricating oil is An opening that faces the space on the case side, and an oil supply pipe that opens below the level of the lubricating oil stored in the lower portion of the space on the case side is connected to the oil supply port. To do.

  One end of the case protrudes toward the center of the rotating shaft, and the outer peripheral edge of the side block on the case side is in contact with the inner peripheral edge of the opening of the case. Further, the oil supply port of the lubricating oil passage is positioned higher than the oil supply port in the conventional gas compressor.

  For this reason, depending on the amount of lubricating oil stored in the space on the case side, that is, in the discharge chamber, the level of the lubricating oil may be lower than the oil supply port. Thus, when the liquid level of the lubricating oil falls below the oil supply port, it becomes impossible to supply the lubricating oil from the oil supply port to the lubricating oil passage, and the lubrication of the portion requiring lubrication becomes insufficient. There is a fear.

  Moreover, in a vane rotary type gas compressor, there exists a possibility that a vane back pressure cannot be obtained appropriately.

  In this regard, the gas compressor of the present invention is connected to the oil supply port with an oil supply pipe that opens below the liquid level of the lubricant stored in the lower part of the space on the case side. Even when the liquid level of the oil is lower than the oil supply port, the opening of the oil supply pipe is located below the liquid level of the lubricant, so that the lubricant is supplied to the lubricating oil passage through the oil supply pipe. It is possible to prevent the lubrication performance from deteriorating.

  On the other hand, the gas compressor according to a sixth aspect of the present invention is the gas compressor according to any one of the first to fourth aspects, wherein the overhang of the one end portion of the case toward the center of the rotating shaft is an opening. It is formed in the part except the lower edge part.

  In the gas compressor formed in this way, the bottom surface and the lower edge of the opening are substantially the same height in the case, so even if the oil filler port is formed on the lower surface of the compressor body, This oil filler port can be kept at a position slightly higher than the lower edge of the opening, i.e. slightly higher than the bottom surface in the case, and until the liquid level of the lubricating oil drops to the vicinity of the bottom surface in the case, Lubricating oil can be properly supplied from the oil supply port, and lubrication performance can be ensured without providing an oil supply pipe.

  According to the gas compressor according to the present invention, since one end portion forming the opening of the case protrudes toward the center direction of the rotating shaft and the opening area of the case is reduced, the load acting on the support member is reduced. Reduced.

  Moreover, since only one end of the case is overhanging, the volume inside the case is not significantly reduced, and the flow velocity of the discharge gas in the space inside the case that occurs when the volume is greatly reduced. It is possible to avoid the effect of suppressing the lowering of the pressure, to prevent the separation performance of the lubricating oil from the gas from being impaired, and to obtain the vane back pressure appropriately.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, the best embodiment of the gas compressor of the invention will be described with reference to the drawings.

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

  In the illustrated compressor 100, the compressor main body is driven by an electric motor 90 built in the housing 10, and is used in an air conditioning system mounted on a vehicle. The compressor 100 uses carbon dioxide gas (R744) as a refrigerant. It sucks in as gas G (gas), compresses the refrigerant gas G, and discharges the compressed refrigerant gas G.

  Specifically, an electric motor 90 is disposed therein, and a housing 10 including a motor housing 13 having one end opened in a direction in which the rotation shaft 91 of the electric motor 90 extends and a case 11 having one end opened. The compressor main body having a rotating shaft 51 that rotates integrally with the rotating shaft 91 of the electric motor 90 and one end of the case 11 are fastened so that the opening of the motor housing 13 and the opening of the case 11 face each other. The internal space of the housing 10 formed in a state where the both bolts 11 and 13 are fastened by the fastening bolt 71 is divided into a space on the motor housing 13 side and a space on the case 11 side, and is disposed in the space on the case 11 side. As shown in FIG. 2, the compressor main body is provided with a center plate 12 (support member) that holds the compressor body by six bolts 73.

  Here, as shown in the cross-sectional view of FIG. 2, the center plate 12 is fastened and fixed to one end of the case 11 by five hexagon socket bolts 72 (fastening members), and as shown in FIG. In addition, it has a substantially hat-shaped cross section, and the convex portion of the hat-shaped cross section is disposed so as to enter a space formed on the inner peripheral side of the stator of the electric motor 90.

  As described above, with respect to the axial direction of the rotating shafts 51 and 91, the center plate 12 is partly inserted into the space that is actually a gap in the space occupied by the electric motor 90. The space utilization efficiency along the axial direction of the shafts 51 and 91 can be improved, and the length of the compressor 100 along the axial direction is shortened. Reference numeral 92 denotes a terminal provided with electrical wiring to which electric power for driving the electric motor 90 is supplied.

  The compressor main body includes a rotor 50 (rotary body) that rotates around the rotation shaft 51 integrally with the rotation shaft 51, and a cylinder 40 that has an elliptical cross-sectional outline on the inner peripheral surface that covers the outer periphery of the rotor 50. The two side blocks (front side block 20 and rear side block 30) sandwiching the rotor 50 and the cylinder 40 from the both end surfaces, respectively, and a plurality of unillustrated projections that can project from the rotor 50 toward the inner peripheral surface of the cylinder 40. It is the structure provided with the vane.

  As the rotor 50 rotates, the volume of the space (compression chamber) surrounded by the rotor 50, the cylinder 40, the two side blocks 20, 30 and the two vanes before and after the rotation direction changes periodically. The refrigerant gas G (gas) sucked into the compression chamber is compressed to a high pressure and discharged.

  The rotating shaft 91 of the electric motor 90 and the rotating shaft 51 of the compressor main body may be physically separate members or may be integrally formed.

  The motor housing 13 is formed with a suction port 14 for taking in the refrigerant gas G from the outside. The gas G sucked from the suction port 14 is outside the space occupied by the electric motor 90 in the internal space on the motor housing 13 side. To the void space (suction chamber) 15.

  On the other hand, the case 11 is formed with a discharge port 17 for discharging the compressed gas G to the outside, and the high-pressure refrigerant gas G discharged from the compressor body is occupied by the compressor body in the space on the case 11 side. The ink is discharged from the discharge port 17 to the outside through a space (discharge chamber) 16 other than the space.

  Then, the refrigerant gas G supplied to the suction chamber 15 is sucked into the compressor body through the vent hole 12 a formed in the center plate 12 and compressed to a high pressure, and discharged from the discharge port 17 through the discharge chamber 16. Is done.

  The center plate 12 covers the outer side of the side block on the side of the center plate 12, that is, the front side block 20 and the cylinder 40, and the side block on the side of the case 11, that is, the rear side block 30. Is in contact with the inner peripheral edge of the opening 11c of the case 11 (see FIG. 3).

  In FIG. 1, one end of the rotating shaft 91 of the electric motor 90 is pivotally supported on the motor housing 13 by a ball bearing 93. The rear side block 30 of the compressor body has an oil separator (not shown) that is a wire mesh for separating the refrigerating machine oil R mixed in the refrigerant gas G discharged from the compression chamber into the discharge chamber 16 from the refrigerant gas G. ) Equipped with a cyclone block 60.

  Here, as shown in FIG. 3, the case 11 is formed such that one end portion 11 d forming the opening 11 c protrudes toward the center C direction of the rotation shafts 51 and 91.

  As a result of the end 11d projecting in the direction of the center C, the inner peripheral edge of the projecting portion 11a becomes the opening diameter D2 of the opening 11c, and this opening diameter D2 is an in-plane perpendicular to the center C inside the case 11. The diameter (D2 <D1) is smaller than the space diameter D1.

  Next, the operation of the compressor 100 of this embodiment will be described.

First, the discharge chamber 16, which is the internal space on the case 11 side, has a high pressure because the high-pressure refrigerant gas G is discharged from the compressor body. The internal pressure of the discharge chamber 16 can be regarded as a substantially static pressure p [N / mm ² ] instantaneously. The compressor body facing the discharge chamber 16, that is, the cyclone block 60 and the rear side block 30, A load F (= pS) in the direction along the rotation axis 51 according to the area S of the 11 openings 11c acts.

  Since the area S of the opening 11c of the case 11 depends on the opening diameter D2, if the opening diameter D2 is large, the opening area S is large, and therefore the acting load F is large. On the other hand, if the opening diameter D2 is small, the opening area is large. S is small, so the acting load F is small.

  And the load F along the direction of the rotating shaft 51 which acted on the compressor main body acts on the center plate 12 which supports this compressor main body. At this time, the load acting on the center plate 12 along the direction of the rotation shaft 51 is in accordance with the load F acting on the compressor main body (when the frictional force or the like is not taken into consideration, it is considered to be substantially equal to the load F) be able to.).

  The load acting on the center plate 12 acts as a tensile load on the hexagon socket head bolt 72 that fastens the center plate 12 and the case 11.

  Here, the opening diameter D2 of the case 11 in the compressor 100 according to the present embodiment is not equal to the space diameter D1 inside the case 11 unlike the conventional compressor, and is smaller than the space diameter D1 inside the case 11. Therefore, the tensile load acting on the hexagon socket head bolt 72 is reduced as compared with the conventional compressor.

  Therefore, the number of hexagon socket head bolts 72 used can be reduced, or thinner bolts can be used, thereby reducing the weight of the compressor 100 and reducing the manufacturing cost.

  In addition, since only a part of the one end portion 11d (the overhang portion 11a) of the case 11 is overhanging, the volume inside the case 11 is not significantly reduced, and as a result, the volume is greatly reduced. It is possible to avoid the effect of suppressing the decrease in the flow rate of the refrigerant gas G in the discharge chamber 16 that occurs in some cases. Therefore, it is possible to prevent the separation performance of the refrigerating machine oil R from being lowered due to the reduction in the flow rate of the refrigerant gas G in the discharge chamber 16.

  Further, in the compressor 100 according to the present embodiment, since the compression target gas is a high-pressure operating refrigerant gas (carbon dioxide gas (R744)), the pressure of the refrigerant gas G discharged from the compressor body is the traditional tradition. The pressure inside the discharge chamber 16 is much higher than that using a general chlorofluorocarbon gas or the like, which is a typical refrigerant gas.

  For this reason, when the load F along the direction in which the rotating shaft 51 acting on the center plate 12 extends becomes high, the load reducing effect described above is more remarkably exhibited.

  In addition, since the compressor main body that compresses the refrigerant gas G with such a high pressure operation can obtain a high discharge pressure, a desired discharge pressure can be obtained even if the size of the compressor main body is reduced. It is easy to use. Therefore, when the end portion 11d of the case 11 is projected toward the center C direction of the rotating shaft 51 to reduce the opening area S of the case 11, even if the size of the compressor main body is reduced accordingly, the desired size can be obtained. The discharge pressure can be ensured.

  Further, the compressor 100 according to the present embodiment includes a rotor 50 in which the compressor body rotates integrally with the rotary shaft 51 around the rotary shaft 51, a cylinder 40 that covers the outer peripheral surface of the rotor 50, and the rotor Vane including two side blocks 20 and 30 that sandwich 50 and cylinder 40 from both end surfaces of rotor 50 and cylinder 40, and a plurality of vanes that can project from rotor 50 toward the inner circumferential surface of cylinder 40. Although this is a rotary type gas compressor, the compressor 100 of this type has a suction chamber 15 in which the refrigerant gas G to be sucked into the compressor body, that is, the compression chamber, and a high-pressure refrigerant gas G are discharged from the compression chamber. The discharge chamber 16 is disposed on the opposite side of the compressor body with respect to the direction in which the rotating shaft 51 extends.

  Since the suction chamber 15 has a low pressure and the discharge chamber 16 has a high pressure, the compressor body is essentially easily pressed from the discharge chamber 16 side to the suction chamber 15 side due to the pressure balance between the chamber pressures. It has become.

  Therefore, the load applied to the center plate 12 is large, and therefore the effect of reducing the load applied to the center plate 12 produced by the compressor 100 of the present embodiment can be made more remarkable.

  Note that, in the compressor 100 according to the present embodiment, the upper portion in the figure of the one end portion 11d of the case 11 mainly protrudes largely toward the center C, and the amount of protrusion in the lower portion in the figure is the upper protrusion portion. Although it is set to be relatively small compared to 11a, the lower overhanging portion 11a may be overhanged toward the center C in the same manner as the upper overhanging portion 11a.

  In this case, the opening area of the case 11 can be further reduced, and the load applied to the hexagon socket head bolt 72 can be further reduced.

  However, in this case, the position of the lower end portion of the rear side block 30 moves upward in the figure as shown in FIG. 4 (a) as the amount of overhang of the lower overhang portion 11a of the case 11 increases.

  Here, the rear side block 30 is formed with an oil passage 32 (lubricating oil passage) that is a passage for the refrigerating machine oil R stored in the discharge chamber 16, and the oil passage 32 is formed at the lower end of the rear side block 30. An intake port 31 (oil supply port) for taking in the refrigerating machine oil R is opened facing the discharge chamber 16.

  The refrigerating machine oil R that has passed through the oil passage 32 is used for lubrication of each part of the compressor body and back pressure supply to the vanes of the compressor body, but the amount of refrigerating machine oil R stored in the discharge chamber 16 is small. When the amount is small, the intake 31 formed at the lower end of the rear side block 30 tends to be higher than the liquid level of the stored refrigerating machine oil R, and lubrication and back pressure supply can be performed appropriately. There is a risk of disappearing.

  Therefore, it is preferable to employ a configuration in which an oil supply pipe 33 that opens below the liquid level of the refrigerating machine oil R stored in the lower portion of the discharge chamber 16 is connected to the intake 31.

  As described above, since the oil supply pipe 33 is connected to the intake port 31, the lower opening of the oil supply pipe 33 is opened even when the liquid level of the refrigerating machine oil R is lower than the intake port 31. Since it is below the liquid level of the refrigerating machine oil R, it is possible to supply the refrigerating machine oil R to the oil passage 32 via the oil supply pipe 33 and to prevent the lubrication performance and the back pressure supply performance from being deteriorated. it can.

  In addition, the compressor 100 according to the present embodiment includes the electric motor 90 inside the housing 10. For this reason, the center plate 12 divides the internal space on the electric motor 90 side and the internal space on the case 11 side. Although it is a structure which partitions off, the gas compressor of this invention is not limited to this structure, The gas compressor which obtains a driving force from the outside, without providing the electric motor 90 may be sufficient.

  The gas compressor that does not include the electric motor 90 does not include the center plate 12 that partitions the internal space, but is fastened to one end of the case 11 as in the compressor 100 shown in FIG. The front head 12 ′ that holds the compressor main body (rotary shaft 51, rotor 50, cylinder 40, front side block 20, rear side block 30, etc.) disposed in the internal space surrounded by Since the same function as the center plate 12 is achieved, such a compressor 100 can also be an embodiment of the gas compressor according to the present invention.

  In addition, each code | symbol of the compressor 100 shown in FIG. 5 respond | corresponds to each component of the same code | symbol shown in FIG. Reference numeral 80 denotes an electromagnetic clutch that transmits power received from a power supply source such as an in-vehicle engine to the rotating shaft 51.

  Even in the compressor 100 according to the embodiment configured as described above, one end portion of the case 11 is formed so as to project in the direction of the rotation shaft 51 as in the compressor 100 illustrated in FIG. The opening area of the case 11 defined by the inner peripheral edge can be made smaller than before.

  Therefore, the load acting on the front head 12 ′ (support member) can be reduced, and the tensile load acting on the hexagon socket bolt 72 that fastens the front head 12 ′ and the case 11 can be reduced.

  Furthermore, since only the overhanging portion 11a of the case 11 is overhanging, the internal volume of the case 11 is not significantly reduced. As a result, the refrigerant in the discharge chamber 16 generated when the volume is greatly reduced. The effect of suppressing the decrease in the flow rate of the gas G can be avoided. Therefore, it is possible to prevent the separation performance of the refrigerating machine oil R from being lowered due to the reduction in the flow rate of the refrigerant gas G in the discharge chamber 16.

  Other effects can also be exhibited in the same manner as the compressor 100 shown in FIG.

  In the compressor 100 of each embodiment described above, the entire circumference of the opening of the one end portion 11d of the case 11 projects toward the center C. However, instead of forming a projecting portion around the entire circumference of the opening, for example, FIG. As shown in the figure, a form in which the overhang portion is formed in a portion excluding the lower edge portion of the opening 11c, that is, a form in which the overhang amount of the lower overhang portion 11a is 0 (zero) can also be adopted.

  Thus, in the compressor 100 in which the extension amount of the lower extension portion 11a is zero, the bottom surface of the discharge chamber 16 inside the case 11 and the lower edge of the opening 11c have the same height, and therefore, the lower surface of the compressor body. The intake port 31 formed at the bottom of the opening 1c can be kept at a position slightly higher than the lower edge of the opening 1c, that is, a position slightly higher than the bottom surface of the discharge chamber 16. Until it decreases to the vicinity of the bottom surface, the refrigerating machine oil R can be properly supplied from the intake 31, and the lubrication performance and the vane back pressure can be sufficiently secured without providing the oil supply pipe 33.

It is sectional drawing which shows the vane rotary type compressor which is one Embodiment of the gas compressor which concerns on this invention. It is sectional drawing which shows the cross section along the AA line of the compressor shown in FIG. It is a figure which shows only the case of the compressor shown in FIG. In the compressor shown in FIG. 1, it is a figure which shows the modification which enlarged the overhang | projection amount of the lower overhang | projection part of a case edge part, (a) points out the problem in that case, (b) is the figure It is a figure which shows the modification which solves a problem. It is a figure which shows embodiment about the gas compressor of the format which is not equipped with an electric motor. In the compressor shown in FIG. 1, it is a figure which shows the modification which made the overhang | projection amount of the lower overhang | projection part of the case edge part 0 (zero), (a) is sectional drawing equivalent to FIG. 1, (b) is. It is sectional drawing which shows the cross section along the BB line in (a). It is a figure which shows the conventional gas compressor.

Explanation of symbols

10 Housing 11 Case 11a Overhanging portion 12 Center plate (supporting member)
12a Ventilation hole 13 Motor housing 14 Suction port 15 Suction chamber 16 Discharge chamber 17 Discharge port 20 Front side block 30 Rear side block 40 Cylinder 50 Rotor 51 Rotating shaft 60 Cyclone block 71 Hexagon socket head cap screw (fastening member)
72 Fastening bolt 90 Electric motor 100 Compressor (gas compressor)
G Refrigerant gas R Refrigeration machine oil

Claims (6)

A compressor main body having a rotating shaft, a case having one end side opened in the direction in which the rotating shaft extends, and an inner space that is fastened to the one end of the case and surrounded by the case. A gas compressor that discharges the gas compressed by the compressor main body into the space inside the case, the support member holding the compressor main body installed
The gas compressor according to claim 1, wherein the one end portion of the case projects toward a center direction of the rotation shaft to reduce an opening area of the case. A compression housing including a motor housing having one end opened in a direction in which the rotating shaft of the electric motor housed therein is open, a case having one open end, and a rotating shaft that rotates integrally with the rotating shaft of the electric motor. The internal space formed by the machine main body and the one end portion of the case facing each other and the opening of the motor housing and the opening of the case facing each other is defined as a space on the motor housing side and a space on the case side. And a support member that holds the compressor body disposed in the space on the case side, and gas in the space on the motor housing side is formed in the support member via a vent hole. In the gas compressor that sucks and compresses the compressor body, and discharges the compressed gas to the space on the case side,
The gas compressor according to claim 1, wherein the one end portion of the case projects toward a center direction of the rotation shaft to reduce an opening area of the case.   The gas compressor according to claim 1, wherein the gas is a high-pressure operating refrigerant gas. The compressor body includes a rotating body that rotates integrally with the rotating shaft around the rotating shaft, a cylinder that covers an outer peripheral surface of the rotating body, the rotating body and the cylinder, and the rotating body and the cylinder. Two side blocks sandwiched from both end surface sides of the cylinder, and a plurality of vanes capable of projecting from the rotating body toward the inner peripheral surface of the cylinder,
The support member covers a side block on the support member side of the two side blocks and the outside of the cylinder, and an outer peripheral edge portion of the side block on the case side of the two side blocks is The gas compressor according to any one of claims 1 to 3, wherein the gas compressor is in contact with an inner peripheral edge of an opening of the case.   A lubricating oil passage is formed in the side block on the case side, and an oil supply port of the lubricating oil passage opens toward the space on the case side, and the space on the case side is opened to the oil supply port. The gas compressor according to claim 4, wherein an oil supply pipe that opens below a liquid surface of the lubricating oil stored in the lower part of the oil compressor is connected. The overhang of the one end portion of the case toward the center of the rotating shaft is formed in a portion excluding a lower edge portion of the opening. The gas compressor according to item.

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