JP2012233464A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor capable of effectively preventing ingress of liquid refrigerant into an intake aperture when the level of the liquid refrigerant in an intake chamber is elevated irrespective of the contour shape or the size along the width direction of the intake chamber.SOLUTION: The gas compressor includes a compressor body 70 having a compression chamber 48 for compressing supplied refrigerant gas G into high-pressure compressed gas, and a housing 10 which houses the compressor body 70, and has an intake chamber 31 in which the refrigerant gas G to be sucked in the compression chamber 48 between the compressor body 70 and the housing 10 itself. An intake aperture 32 for communicating the intake chamber 31 with the compression chamber 48 is formed in a front side block 30 (a wall part) adjacent to the intake chamber 31 and the compression chamber 48 in the compressor body 70. A duct 34 with both ends 34a, 34b thereof being opened is provided in the intake chamber 31 so that an opening of the lower end 34b out of both ends 34a, 34b may be communicated with the lower intake aperture 32 in a watertight manner, and an opening of the upper end 34a may be located higher than the intake aperture 32.

Description

  The present invention relates to a gas compressor, and in particular, to an improvement in a passage for a gas supplied to a compression chamber.

  Conventionally, a gas compressor (compressor) having a compression chamber that compresses a supplied gas such as a refrigerant gas into a high-pressure compressed gas is used in an air conditioning system (hereinafter referred to as an air conditioning system).

  Here, for example, in a vane rotary type compressor, the compressor body having a compression chamber that compresses the supplied refrigerant gas into a high-pressure compressed gas, and the compressor body is covered, and the compressor body is interposed between the compressor body and the compressor body. And a housing having a suction chamber into which the refrigerant gas to be sucked is introduced.

  In the compressor body, the suction chamber and a wall portion (side block or the like) adjacent to the compression chamber is formed with a suction window through which the suction chamber and the compression chamber are passed, and the refrigerant gas introduced into the compressor Is sucked into a suction chamber defined by the housing and the compressor body, and is supplied from the suction chamber to the compression chamber through a suction window.

  By the way, when the operation of the air conditioning system provided with the compressor is stopped and the ambient atmosphere temperature is lowered, the refrigerant gas circulating inside the air conditioning system is liquefied to become a liquid refrigerant, and this liquid refrigerant becomes the compressor. Into the suction chamber.

  Since the liquid refrigerant flowing into the suction chamber accumulates in the suction chamber, the liquid level in the suction chamber becomes high, and when the liquid level exceeds the lowest position of the suction window, the liquid refrigerant collected in the suction chamber. Flowed into the compression chamber through the suction window.

  However, when the liquid refrigerant flows into the compression chamber, liquid compression occurs in the compression chamber, which may cause abnormal noise or damage.

  Therefore, a partition plate extending to a position higher than the suction window is provided at the bottom of the suction chamber. Even if the liquid level rises in the region outside the partition plate in the suction chamber, the partition plate is located on the inner side (suction window). A technique has been proposed in which the liquid refrigerant does not easily flow from the suction window into the compression chamber so that the liquid level does not rise in the region close to) (Patent Document 1).

Japanese Utility Model Publication No. 6-80887

  However, the partition plate described above prevents the liquid level from rising in a region close to the suction window, and this is a technique for causing the partition plate to function as a bank.

  That is, in order to prevent liquid refrigerant from entering the suction window with such a partition plate, it is necessary to prevent liquid refrigerant from entering the entire area of the suction chamber near the suction window. It is necessary to extend the partition plate over the entire width.

  For this reason, the outer shape of the partition plate also needs to match the contour shape of the suction chamber and the size along the width direction, but the contour shape of the suction chamber and the size along the width direction are various. Therefore, it is necessary to prepare many types of partition plates for each type of compressor specification.

  Further, the height of the partition plate may not be arbitrarily set, and there is a possibility that a practical effect cannot be obtained if the liquid refrigerant has a large increase in the liquid level.

  The present invention has been made in view of the above circumstances. Regardless of the outline shape of the suction chamber and the size along the width direction, the liquid to the suction window is increased with respect to the rise in the liquid level of the liquid refrigerant in the suction chamber. It is an object of the present invention to provide a gas compressor that can effectively prevent the refrigerant from entering.

  The gas compressor according to the present invention is provided with a duct extending upward in the suction window, and even if the liquid level of the liquid refrigerant entering the suction chamber rises, the liquid level exceeds the opening at the upper end of the duct. Until, the liquid refrigerant is prevented from entering the suction window.

  That is, the gas compressor according to the present invention covers a compressor main body having a compression chamber that compresses supplied gas into high-pressure compressed gas, and the compressor main body, and is sucked into the compression chamber between the compressor main body. And a housing formed with a suction chamber into which the gas to be introduced is formed, and a suction window that allows the suction chamber and the compression chamber to pass through is formed in the compressor body, adjacent to the suction chamber and the compression chamber, A duct with an opening is provided in the suction chamber so that the opening at one end of both ends communicates with the suction window in a watertight manner, and the opening at the other end is positioned higher than the suction window. It is characterized by.

  According to the gas compressor of the present invention, regardless of the contour shape of the suction chamber and the size along the width direction, the liquid refrigerant enters the suction window with respect to the rise of the liquid refrigerant level in the suction chamber. Can be effectively prevented or suppressed.

It is a figure which shows the external appearance of the vane rotary type compressor which is one Embodiment of the gas compressor which concerns on this invention. It is a longitudinal cross-sectional view of the compressor shown in FIG. It is a cross-sectional view which shows the cross section along the AA in FIG. FIG. 3 is a view of the compressor body viewed from the direction of arrow B with the front head 12 in FIG. 2 removed. It is a perspective view which shows the detail of the duct shown in FIG. It is a perspective view which shows the example of the duct whose shape of the opening of an edge part is circular.

  Hereinafter, an embodiment according to the gas compressor of the present invention will be described with reference to the drawings.

  FIG. 1 is a view showing an appearance of a vane rotary compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of a gas compressor according to the present invention, and FIG. 2 is a longitudinal sectional view of the compressor 100 shown in FIG. 3 is a cross-sectional view showing a cross section taken along the line AA in FIG. 2, and FIG. 4 is a view of the compressor main body 70 as viewed in the direction of arrow B with the front head 12 removed in FIG.

  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 to the condenser of the air conditioning system.

  The condenser heat-exchanges the compressed refrigerant gas G with ambient air and the like to dissipate heat from the refrigerant gas G and liquefy it, 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 accompanying the vaporization of the refrigerant.

  The vaporized low-pressure refrigerant gas G returns to the compressor 100 and is compressed, and the above steps are repeated thereafter.

  The compressor 100 houses the compressor body 70 inside the housing 10.

  The housing 10 includes a case 11 having a substantially cylindrical shape with one end closed and the other end opened, and a front head 12 covering the other open end of the case 11, and the front head 12 is the case 11. In the assembled state, a space for accommodating the compressor main body 70 is formed inside the housing 10, and the compressor main body 70 is accommodated to cover the compressor main body 70.

  The front head 12 is formed with a suction port 12a for taking in the low-pressure refrigerant gas G supplied from the evaporator, and the case 11 condenses the high-pressure refrigerant gas G compressed by the compressor body 70. A discharge port 11a for discharging to the container is formed.

  As shown in FIG. 3, the compressor body 70 includes a rotary shaft 51 that is driven to rotate in the direction of the arrow around the axis, a columnar rotor 50 that rotates integrally with the rotary shaft 51, and an outer peripheral surface of the rotor 50. A cylinder 40 having a substantially elliptical inner peripheral surface 49 surrounding the outer side and open at both ends, and embedded in the outer periphery of the rotor 50 so as to protrude outwardly, and the tip of the protruding side is a cylinder The amount of protrusion is variable so as to follow the contour shape of the inner peripheral surface 49 of 40, five plate-like vanes 58 embedded in the rotor 50 at equal angular intervals around the rotation shaft 51, and both sides of the cylinder 40 A front side block 30 and a rear side block 20 fixed so as to cover the open end surface from the outside of the open end surface, respectively, and a cyclone block 60 attached to the rear side block 20 are provided. .

  The volume of the five compression chambers 48 partitioned by the two side blocks 20 and 30, the rotor 50, the cylinder 40, and the two vanes 58 and 58 that follow each other along the rotation direction of the rotation shaft 51 is the rotation shaft. By repeating the increase / decrease in accordance with the rotation of 51, the refrigerant gas G sucked into the compression chamber 48 in the suction process is compressed through the two suction windows 32, 33 formed in the front side block 30, and the cylinder 40 and the rear side block 20 are configured to discharge into the discharge chamber 21.

  One of the portions of the rotating shaft 51 protruding from both end surfaces of the rotor 50 is rotatably supported by the bearing portion of the front side block 30 and penetrates the front head 12 to the outside. And is connected to a driving force transmission unit 80 (for example, a pulley) to which external power (not shown) is transmitted.

  The other side of the protruding portion of the rotating shaft 51 is rotatably supported by the bearing portion of the rear side block 20.

  The discharge chamber 21 into which the compressed high-pressure refrigerant gas G is discharged is a space defined by the case 11 and the compressor main body 70, and the discharge port 11 a described above directly communicates with the discharge chamber 21.

  Refrigerating machine oil R is stored at the bottom of the discharge chamber 21. The refrigerating machine oil R gives back pressure for causing the vane 58 to protrude, lubricating oil between the vane 58 and the rotor 50 and the cylinder 40, lubricating oil between the rotor 50 and each side block 20, 30, and the like. It acts as.

  The refrigerating machine oil R is supplied into the compressor main body 70 through an oil guide passage formed in the rear side block 20, the cylinder 40, the front side block 30, and the like.

  A part of the refrigerating machine oil R supplied to the inside of the compressor main body 70 is mixed in the refrigerant gas G in the compression chamber 48 and discharged from the compression chamber 48 together with the refrigerant gas G. The refrigerating machine oil R passes through the cyclone block 60 before entering the discharge chamber 21.

  The refrigerating machine oil R is separated from the refrigerant gas G by the centrifugal force acting when passing through the cyclone block 60 and stored in the bottom of the discharge chamber 21.

  On the other hand, the refrigerant gas G from which the refrigerating machine oil R is separated is discharged from the discharge chamber 21 to the outside of the compressor 100 through the discharge port 11a.

  On the other hand, the low-pressure refrigerant gas G introduced into the compressor 100 from the suction port 12 a is introduced into the suction chamber 31 that is a space defined by the front head 12 and the front side block 30.

  Then, the refrigerant gas G introduced into the suction chamber 31 is sucked so as to pass through the suction chamber 31 and the compression chamber 48 through the front side block 30 (wall portion) adjacent to the suction chamber 31 and the compression chamber 48. It is introduced into the compression chamber 48 through the windows 32 and 33.

  Here, the rotor 50 has a columnar shape, the outer contour of the inner peripheral surface 49 of the cylinder 40 is substantially elliptical, and the rotor 50 is disposed so as to be in contact with the substantially short diameter portion of the inner peripheral surface 49 of the cylinder 40. Therefore, the space defined by the outer peripheral surface of the rotor 50 and the inner peripheral surface 49 of the cylinder 40 and serving as the compression chamber 48 is formed at two points symmetrical with respect to the rotation shaft 51.

  The compression chambers 48 that change in volume from the suction stroke to the compression stroke are formed in these two spaces, respectively, so that the suction windows 32 and 33 are positioned symmetrically with respect to each space. Is formed.

  Further, the outline shapes of the suction windows 32 and 33 define the suction start timing and the suction end timing of the refrigerant gas G depending on the positional relationship with the rotating vane 58, and therefore have substantially the same shape. .

  As described above, since the two spaces serving as the compression chambers are located at different heights, one of the two suction windows 32 and 33 is located at a position lower than the other. The heights of the suction windows 32 and 33 (particularly the lower edges of the suction windows 32 and 33) vary depending on the posture and the like when the compressor 100 is installed in a vehicle or the like. , 33 are extremely rare in height, and one of the positions is often lowered.

  When the suction windows 32 and 33 are arranged in the posture shown in FIG. 1, a tubular (for example, snorkel) duct 34 is provided around the suction window 32 whose height position from the horizontal plane is lowered. Is attached.

  For example, as shown in the perspective view of FIG. 5, the duct 34 is a hollow tube formed by bending in an approximately L shape, and both end portions 34 a and 34 b are opened, and both end portions 34 a and 34 b are opened. Between the openings, gas and liquid can freely flow through the hollow interior.

  The duct 34 is formed by rounding a metal plate (plate-like member) into an annular shape, and the edge portions 34c and 34d of the plate-like body are formed in a part of the circumference. It is superimposed.

  The overlapped edge portions 34c and 34d can be displaced from each other along the circumferential direction, and when elastically deformed so as to widen the overlapping range from the wound state, the outer peripheral length is shortened, When the overlapping range is restored to the original width by the elastic force corresponding to the elastic deformation, the outer peripheral length returns to the original length.

  Of the both end portions 34a and 34b of the duct 34, the end portion 34b which is the lower side in the posture shown in FIG. 5 and opens toward the vertical plane is formed in the suction window 32 as shown in FIGS. It is fitted.

  That is, the end 34b of the duct 34 is elastically deformed so that the overlapping range of the end edges 34c and 34d is widened, so that the area of the opening of the end 34b is narrowed. Thus, the end 34 b is inserted into the suction window 32.

  Then, in a state where the end portion 34b is inserted into the suction window 32, the elastic deformation is released, so that the overlapping range of the end edge portions 34c and 34d becomes narrow as originally, that is, the end portion 34b. In the process of restoring, the outer peripheral surface of the end portion 34b is in close contact with the outer periphery of the suction window 32, and the outer peripheral surface of the end portion 34b and the suction window 32 due to this close contact are in close contact with each other. The duct 34 is held on the front side block 30 in the posture shown in FIG.

  In addition, when the outer peripheral surface of the end portion 34b and the outer periphery of the suction window 32 are in close contact with each other, the opening of the end portion 34b communicates with the suction window 32 in a watertight manner. Therefore, the liquid refrigerant L does not enter the suction window 32 from the gap between the outer peripheral surface of the end portion 34 b and the outer periphery of the suction window 32.

  As a result, the lower suction window 32 does not directly face the suction chamber 31 like the upper suction window 33 but faces the hollow space inside the duct 34. Since the inside communicates with the opening facing the suction chamber 31 only at the upper end portion 34 a of the duct 34, the refrigerant gas G and the like sucked into the suction chamber 31 flows from the opening of the upper end portion 34 a of the duct 34. The passage extending from the hollow interior of the duct 34 to the opening of the lower end 34 b reaches the suction window 32 as a passage, and is sucked into the lower compression chamber 48 from the suction window 32.

  On the other hand, since the upper suction window 33 faces the suction chamber 31, the refrigerant gas G or the like in the suction chamber 31 is directly sucked from the suction chamber 31 through the suction window 33 into the upper compression chamber 48.

  The height from the lower end edge of the duct 34 (the position of the lowest part of the lower end 34b) to the upper end edge (the position of the opening of the upper end 34a) is the height h as shown in FIG. In the state shown in FIG. 4 in which the duct 34 is attached to the lower suction window 32, the upper edge of the duct 34 (the upper edge) is moved from the lowest position of the lower suction window 32 to the height h. The position of the opening of the end portion 34a) is arranged.

  Further, the upper end edge of the duct 34 (the position of the opening of the upper end portion 34 a) is set to be the same height as the lowest portion of the upper suction window 33.

  Here, when the operation of the air conditioning system including the compressor 100 is stopped and the ambient temperature is lowered, the refrigerant gas G circulating in the air conditioning system is liquefied to become the liquid refrigerant L, The liquid refrigerant L flows into the suction chamber 31 through the suction port 12a of the compressor 100.

  Since the liquid refrigerant L flowing into the suction chamber 31 accumulates in the suction chamber 31, the liquid level in the suction chamber 31 increases and is formed in the front side block like a conventional compressor. If the suction window faces the suction chamber directly, the liquid refrigerant passes through the lower suction window with the liquid refrigerant level in the suction chamber above the lowest position of the lower suction window. Was flowing into the compression chamber.

  However, according to the compressor 100 of the present embodiment, the lower suction window 32 does not directly face the suction chamber 31, and is closed by the duct 34 being attached. Even when the liquid level exceeds the lowest position of the lower suction window 32, the liquid refrigerant L does not flow into the compression chamber 48 through the lower suction window 32.

  Further, the liquid refrigerant L does not flow into the suction window 32 until the liquid level of the liquid refrigerant L in the suction chamber 31 reaches the height of the opening of the upper end portion 34a of the duct 34. When the liquid level of L exceeds the height of the opening of the upper end portion 34a of the duct 34, the liquid refrigerant L flows into the duct 34 from the opening of the upper end portion 34a, and reaches the inside of the lower end portion 34b. From the opening, the air flows into the compression chamber 48 through the suction window 32.

  At the same time, the liquid refrigerant L also flows into the upper suction window 33 located at the same height as the opening of the upper end portion 34 a of the duct 34, and the liquid refrigerant L flows into the upper compression chamber 48.

  As described above, the level of the liquid refrigerant L in the suction chamber 31 when the liquid refrigerant L flows into the compression chamber 48 is such that the compressor 100 of the present embodiment is higher than the conventional compressor by the height h of the duct 34. Can be high.

  Therefore, it is possible to effectively prevent the liquid refrigerant L from flowing into the compression chamber 48 against the rise in the liquid level of the liquid refrigerant L in the suction chamber 31.

  Moreover, since the inflow of the liquid refrigerant L to the suction window 32 can be prevented only by attaching the duct 34 communicating with the suction window 32, the contour shape and the width direction (direction orthogonal to the rotation shaft 51) are provided in the suction chamber 31. Compared with the prior art in which a bank-like partition plate corresponding to the size along the line is provided, the inflow of the liquid refrigerant L can be prevented with a simple structure.

  Further, the duct 34 has the other end 34b formed by rounding a plate-like body in an annular shape, and the annular portion is formed so as to be elastically deformable so as to change its outer peripheral length. The structure is inserted into the suction window 32 in a state of being elastically deformed so that the outer peripheral length thereof is shortened, and is brought into close contact with the outer periphery of the suction window 32 in a restored state of elastic deformation. Can be attached to the compressor main body 70, so that the labor for assembling the duct 34 to the compressor main body 70 can be reduced as compared with a structure in which a fastening member such as a bolt is used.

  Note that the gas compressor of the present invention is not limited to such an assembly structure, but an assembly structure using a fastening member such as the bolt described above, adhesion, welding, and the inner surface of the housing 10 (particularly the front head 12). Various structures such as fixing by sandwiching between the compressor and the compressor main body 70 (particularly, the front side block 30) can be applied.

  In the compressor 100 of the present embodiment, the shape of the opening of the end portion 34b of the duct 34 matches the contour shape of the suction window 32 and is rectangular, but the contour shape of the suction window 32 is circular (true). The shape of the opening of the end portion 34b of the duct 34 is preferably a circular shape that matches the contour shape of the suction window 32 as shown in FIG.

  Thus, in the case where the contour shape of the end portion 34b is circular, the outer peripheral surface of the end portion 34b and the outer periphery of the suction window 32 when returning from the elastically deformed state so as to shorten the outer peripheral length to the restored state. Can be made substantially uniform in the circumferential direction, and the watertightness between the two can be improved.

  The compressor 100 according to the present embodiment has a structure in which the end 34b of the duct 34 is inserted into the suction window 32 and assembled. Therefore, the shape of the opening of the end 34b matches the contour of the suction window 32. However, when this assembly structure is not used, for example, the front side block 30 has a concave-convex shape that engages with each other by using a fastening material or the like on the peripheral portion of the suction window 32 at the end 34b. When the structure is assembled by combination, the shape of the opening of the end 34 b of the duct 34 may not match the contour shape of the suction window 32.

  Further, since the duct 34 of the compressor 100 of the present embodiment has the opening 34a at the same height as the upper suction window 33, as a result, the upper suction window 33 and the lower suction window 33 are disposed. The window 32 is related to the liquid level of the liquid refrigerant L accumulated in the suction chamber 31, and the liquid refrigerant L flows at the same timing. However, the gas compressor of the present invention is limited to this form. It is not a thing.

  That is, for example, the opening of the upper end portion 34 a of the duct 34 may be at a position higher than the center of the rotation shaft 51 provided in the compressor main body 70.

  In an ordinary vane rotary compressor, two spaces serving as compression chambers are formed point-symmetrically with respect to the rotation axis, and thus one space is usually at a lower position than the other space.

  However, the suction window that leads to the compression chamber on the lower position side can also obtain substantially the same effect as when the duct is moved to the height position of the rotary shaft that is intermediate between the two spaces.

  This is the same as the highest liquid level (in the case of a gas compressor in a special state where both spaces are horizontally arranged) when the liquid refrigerant does not flow into any of the suction windows without a duct. Since the liquid refrigerant can be prevented from flowing up to the liquid level, there is a practical effect.

DESCRIPTION OF SYMBOLS 10 Housing 11 Case 12 Front head 30 Front side block 31 Suction chamber 32, 33 Suction window 34 Duct 34a, 34b End part 34c, 34d End edge part 48 Compression chamber 50 Rotor 51 Rotating shaft 70 Compressor main body 100 Vane rotary type compressor G Refrigerant gas (gas)
L Liquid refrigerant (liquid)
R Refrigerating machine oil (oil content)

Claims (5)

A compressor main body having a compression chamber for compressing the supplied gas into a high-pressure compressed gas, and an intake for covering the compressor main body and introducing the gas sucked into the compression chamber between the compressor main body And a housing forming a chamber,
A suction window that allows the suction chamber and the compression chamber to pass through is formed in the suction chamber and a wall portion adjacent to the compression chamber in the compressor body.
The duct having both ends opened so that the opening at one end of the both ends communicates with the suction window in a watertight manner, and the opening at the other end is higher than the suction window. A gas compressor provided in the suction chamber. The compressor body includes two or more of the compression chambers at different height positions,
The suction window is formed for each compression chamber,
2. The gas compressor according to claim 1, wherein the duct is provided corresponding to a suction window formed at least at a height position of the two or more suction windows. .   The gas compression according to claim 1 or 2, wherein the duct is formed so that an opening at the other end is higher than a center of a rotation shaft included in the compressor body. Machine.   The said duct is formed so that opening of said other edge part may become the same height position as the other suction window in which the said duct is not provided correspondingly. Gas compressor.   In the duct, the other end portion is formed by rounding a plate-like member in an annular shape, and the annular portion is formed so as to be elastically deformable so as to change an outer peripheral length thereof. The outer circumferential length is inserted into the suction window in a state of being elastically deformed to be short, and is in close contact with the outer periphery of the suction window in a restored state of the elastic deformation. The gas compressor according to item.