JP2007332850A - Fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid machine capable of making both compatible in securing the sufficient flow passage cross-sectional area of a gas fluid reaching a compression mechanism from a suction port and miniaturizing an external shape. <P>SOLUTION: A scroll compressor 1 is constituted so that a scroll compression mechanism 23 is stored and arranged in a housing 3 having a shape formed in a funnel shape, and a compression mechanism body of the scroll compression mechanism 23 is arranged in a wide port part of a front housing 5, and a compression mechanism driving part is arranged in a narrow part. A recessed part 51 is formed outside a thrust receiving surface 5B positioned on a bottom surface of the wide port part and supporting the compression mechanism. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a fluid machine such as a scroll compressor.

Conventionally, a fluid machine such as a scroll compressor for compressing a gas fluid is known.
Such a fluid machine includes a funnel-shaped low-pressure side housing provided with a suction port for introducing a low-pressure gas fluid, and a high-pressure side housing provided with a discharge port for allowing the high-pressure gas fluid to flow out. There is a housing in which a compression mechanism such as a scroll pressure mechanism is housed and installed in a housing that is sealed by being connected and integrated. In this case, in the funnel-shaped low-pressure side housing, the main body portion of the compression mechanism is disposed on the side of the large-diameter wide portion connected to the high-pressure side housing, and the compression mechanism drive unit such as the rotary shaft has a small diameter It is set as the structure arrange | positioned in the narrow part. (For example, see Patent Document 1)
Japanese Patent No. 3227075 (FIG. 1)

However, in the above-described conventional fluid machine, in order to secure the flow path cross-sectional area of the gas fluid that is introduced into the compression mechanism from the suction port provided in the low-pressure side casing and is compressed, the inner peripheral surface of the low-pressure side casing is compressed. It is necessary to set a large dimension of the gap δ formed between the outer peripheral surface of the mechanism. Since the gap δ increases the diameter on the housing side to ensure the necessary dimensions, the outer dimensions of the fluid machine are increased accordingly, which is an obstacle to miniaturization.
For example, the body of the low-pressure casing is generally manufactured by aluminum die casting. In this case, however, the corner from the side wall surface to the bottom surface has a radius R ₀ to ensure strength.
R shape may be used. Therefore, the gap δ described above is at least δ _0.
(See FIG. 3 (b)) A gap that is set based on the starting position of the flat surface that becomes the thrust receiving surface 5B after completion of the R shape to prevent interference between the body portion 5A and the orbiting scroll member 27. Department was necessary. That is, in order to avoid the interference of orbiting the orbiting scroll with the R shape at the corner portion, the gap δ from the inner peripheral surface of the trunk portion 5A to the sliding range of the orbiting scroll member 27 is δ _0.
This also inevitably increases the appearance size because it needs to be larger. The aluminum die cast body 5A is provided with a small inclination that is a draft for manufacturing reasons, so that the outer shape gradually increases as it goes above the side wall surface, which is useless. The outline was large.

From such a background, there is a demand for a fluid mechanical structure that sufficiently secures a cross-sectional area of the flow path that guides the gas fluid introduced from the suction port to the compression mechanism, and that can be reduced in size by reducing the outer dimensions.
The present invention has been made in view of the above circumstances, and an object of the present invention is to secure sufficient cross-sectional area of the gas fluid from the suction port to the compression mechanism and to reduce the outer shape. It is an object of the present invention to provide a fluid machine that can be used.

In order to solve the above problems, the present invention employs the following means.
In the fluid machine according to the present invention, the compression mechanism is housed and installed in a funnel-shaped housing, the compression mechanism main body of the compression mechanism is disposed in the wide portion of the housing, and the compression mechanism driving unit is narrowed. In the fluid machine arranged in (1), a recess is formed outside the compression mechanism support surface that is located on the bottom surface of the wide portion and supports the compression mechanism.

  According to such a fluid machine, since the concave portion is formed outside the compression mechanism support surface that is located on the bottom surface of the wide portion and supports the compression mechanism, the concave portion functions as a flow path for the gas fluid. Therefore, since the cross-sectional area of the flow path of the gas fluid increases, the size of the gap δ can be reduced and the diameter of the housing can be reduced.

  In the above-described invention, it is preferable that the recess and the inner space of the narrow portion communicate with each other, and thereby, gas can be introduced into the compression mechanism drive unit to improve cooling and lubricity. it can.

In the above invention, it is preferable that the concave portion has an arc shape, which makes it easy to ensure strength at the corner portion of the pressure vessel, and sets the gap portion δ without being substantially affected by the corner portion R. can do.
In this case, it is preferable to form the concave portion with a cast casting surface, and this makes it possible to reduce the number of processing steps.

  In the above invention, if the compression mechanism is a scroll compression mechanism and the compression mechanism support surface is a thrust receiving surface, burrs are less likely to occur during machining of the thrust receiving surface.

In the fluid machine according to the present invention, the compression mechanism is housed and installed in a housing in which the shape of the low pressure side housing provided with the suction port is a funnel shape, and the compression mechanism main body of the compression mechanism is disposed in the wide portion of the low pressure side housing. In the fluid machine in which the compression mechanism driving unit is disposed in the narrow portion, the concave portion is formed outside the thrust receiving surface that is positioned on the bottom surface of the wide portion and supports the compression mechanism. Is.

  According to such a fluid machine, since the concave portion is formed outside the thrust receiving surface that is positioned on the bottom surface of the wide portion and supports the compression mechanism, the concave portion functions as a gas fluid flow path. Therefore, since the cross-sectional area of the flow path of the gas fluid increases, the size of the gap δ can be reduced and the diameter of the housing can be reduced.

  According to the present invention described above, the recess is formed outside the thrust receiving surface that supports the compression mechanism to ensure the gas fluid passage cross-sectional area, thereby reducing the size of the gap and reducing the diameter of the housing. Can do. Accordingly, it is possible to provide a fluid machine that sufficiently secures a cross-sectional area of a flow path that guides the gas fluid introduced from the suction port to the compression mechanism and that can reduce the outer dimension by reducing the size of the gap portion. it can.

Hereinafter, an embodiment of a fluid machine according to the present invention will be described with reference to the drawings.
FIG. 1 shows a cross-sectional view of a scroll compressor 1 used for compressing refrigerant gas or the like as an embodiment of a fluid machine according to the present invention.
The illustrated scroll compressor 1 is a horizontal type that is applied to a refrigeration or air conditioner, in particular, a refrigeration apparatus or an air conditioner for a vehicle, and includes a housing 3 that configures a general outline and accommodates and installs a compression mechanism in an internal space. Have. The housing 3 includes a front housing 5 which is a low-pressure side housing and a rear housing 7 which is a high-pressure side housing, and is fixed in a state in which flange portions provided on each of the housings 3 are tightened together by bolts 9. Moreover, the compression mechanism of the scroll compressor 1 becomes the scroll compression mechanism 23 mentioned later, and is comprised by the compression mechanism main body and the compression mechanism drive part.

Inside the front housing 5, a crankshaft 11 constituting a compression mechanism drive unit is supported through a main bearing 13 and a sub-bearing 15 so as to be rotatable around an axis L. One end side (left side in the figure) of the crankshaft 11 is a small diameter shaft portion 11A, and this small diameter shaft portion 11A penetrates the front housing 5 and protrudes to the left side in FIG. As is well known, an unillustrated electromagnetic clutch, pulley, and the like for receiving power are provided on the protruding portion of the small-diameter shaft portion 11A, and power is transmitted from a drive source such as an engine (not shown) via a V-belt or the like. It will be.
A mechanical seal (lip seal) 17 is installed between the main bearing 13 and the sub-bearing 15 to hermetically seal between the inside of the housing 3 and the atmosphere.

  A large-diameter shaft portion 11B is provided on the other end side (right side in the drawing) of the crankshaft 11. Further, the large-diameter shaft portion 11B has an eccentric pin that is eccentric from the axis L of the crankshaft 11 by a predetermined dimension. 11C is provided integrally. The large-diameter shaft portion 11B and the small-diameter shaft portion 11A are rotatably supported by the front housing 5 via the main bearing 13 and the sub-bearing 15, respectively. The eccentric pin 11C is connected to a drive bush 19 that constitutes a compression mechanism drive unit together with the crankshaft 11 and an orbiting scroll member 27 that constitutes a compressor main body, which will be described later, via a drive bearing 21. Is rotated so that the orbiting scroll member 27 is orbitally driven.

The drive bush 19 is integrally formed with a balance weight 19 </ b> A for removing an unbalanced load that is generated when the orbiting scroll member 27 is orbitally driven. Yes.
In addition, a pair of fixed scroll members 25 and a turning scroll member 27 are incorporated in the housing 3 as a compression mechanism body constituting the scroll compression mechanism 23. The fixed scroll member 25 is composed of an end plate 25A and a spiral wrap 25B standing from the end plate 25A, while the orbiting scroll member 27 is a spiral standing from the end plate 27A and the end plate 27A. And a wrap 27B.

  The pair of fixed scroll members 25 and the orbiting scroll member 27 are assembled in a state where the centers of the fixed scroll member 25 and the orbiting scroll member 27 are separated from each other by the orbiting radius and the spiral wraps 25B and 27B are engaged with each other with a phase difference of 180 degrees. Thus, a pair of compression chambers 29 limited by the end plates 25A and 27A and the spiral wraps 25B and 27B are formed between the scroll members 25 and 27 symmetrically with respect to the center of the scroll. . The fixed scroll member 25 is fixedly installed on the inner surface of the rear housing 7 with bolts 31, and the orbiting scroll member 27 is provided on one end side of the crankshaft 11 on the boss portion provided on the back surface of the end plate 27A. The eccentric pins 11C are connected to each other and are driven to turn.

  Further, the orbiting scroll member 27 is supported by a thrust receiving surface 5B formed on the front housing 5 on the back surface of the end plate 27A, and is interposed between the thrust receiving surface 5B and the back surface of the orbiting scroll member 27. By the rotation prevention mechanism 33 such as the pin ring and Oldham ring, the orbiting scroll member 27 is configured to be revolved and driven with respect to the fixed scroll member 25 while preventing the rotation.

A discharge port 25C that discharges the compressed refrigerant gas is opened at the center of the end plate 25A of the fixed scroll member 25. The discharge port 25C is attached to the end plate 25A via a retainer 35. A discharge reed valve 37 is provided. Further, a seal member 39 such as an O-ring is provided on the back surface side of the end plate 25 </ b> A of the fixed scroll member 25 so as to be in close contact with the inner surface of the rear housing 7. A discharge chamber 41 partitioned from is formed. Thereby, the internal space of the housing 3 excluding the discharge chamber 41 is configured to function as the low-pressure side suction chamber 43. Refrigerant gas returning from the refrigeration cycle is sucked into the suction chamber 43 through the suction port 45 provided in the front housing 5, and is formed between the fixed scroll member 25 and the orbiting scroll member 27 through the suction chamber 43. The refrigerant gas is sucked into the compression chamber 29.
Note that a sealing material 47 such as an O-ring is interposed on the joint surface between the front housing 5 and the rear housing 7 to seal the suction chamber 43 formed in the housing 3 from the atmosphere in an airtight manner.

  A scroll compression mechanism 23 is housed and installed in the front housing 5. The front housing 5 includes a large-diameter barrel 5A that accommodates the fixed scroll member 25 and the orbiting scroll member 27 of the compressor body, and the thrust receiving surface 5B that has a diameter reduced in a radial direction following the barrel 5A. A thrust receiving portion 5C for forming the bearing, and a medium diameter bearing support portion 5E for forming a bearing housing portion 5D for housing the main bearing 13, the diameter of which is further reduced following the thrust receiving portion 5C. A sub-bearing 15 following the bearing support portion 5E and a small-diameter boss portion 5F for installing the mechanical seal 17 are provided, and a funnel shape whose diameter is gradually reduced is formed.

  The rear housing 7 has a dish shape including a recess 7 </ b> A for forming the discharge chamber 41 and an inlay part 7 </ b> B fitted to the opening end of the body part 5 </ b> A of the front housing 5. The sealing material 47 described above is interposed in the inlay portion 7B. The rear housing 7 is connected so as to cover one end opening of the body portion 5A of the front housing 5, and is fixed in a state where the flange portions of the front housing 5 and the rear housing 7 are integrally tightened by bolts 9. .

  In this manner, the scroll compression mechanism 23 is housed and installed in the housing 3 in which the shape of the front housing (low pressure side housing) 5 provided with the suction port 45 is funnel-shaped. The fixed scroll member 25 and the orbiting scroll member 27, which are the compression mechanism main body of the scroll compression mechanism 23, are disposed in the space in the trunk portion 5A, and the compression mechanism driving portion of the scroll compression mechanism 23 including the crankshaft 11 and the like is the trunk portion. The scroll compressor 1 disposed in a narrow portion that is an internal space such as the bearing housing portion 5D having a diameter smaller than 5A has an outer side of the thrust receiving surface 5B that is positioned on the bottom surface of the body portion 5A and supports the scroll compression mechanism 23. A recess 51 is formed in the bottom.

  That is, the thrust receiving portion 5C is located on the bottom surface of a space formed as a wide portion in the body portion 5A of the front housing 5 formed in a funnel shape, and therefore this thrust receiving portion (bottom surface) 5C. On the other hand, a recess 51 is formed at the corner from the wall surface forming the body portion 5A to the thrust receiving portion 5C so as to be outside the thrust receiving surface 5B. For example, as shown in FIG. 2, the recess 51 is formed over the entire outer periphery of the thrust receiving portion 5C. Further, the outer diameter of the thrust receiving portion 5C, that is, the inner diameter of the recess 51 is in a range smaller than the envelope line constituted by the locus of the outer shape when the orbiting scroll member 27 is driven. Is installed in a range that does not come into contact even when the orbiting scroll member 27 is driven.

The recess 51 has a curved cross-sectional shape extending from the wall surface forming the body portion 5A to the thrust receiving portion 5C. In particular, as shown in FIG. . The cylindrical wall surface that forms the body portion 5A is an inclined surface with a draft that gradually increases in diameter as it moves away from the thrust receiving portion 5C toward the opening in consideration of a die-cutting operation during casting. Therefore, a concave portion 51 having an arc shape with a radius R is formed so as to continue smoothly from the inclined surface.
Such a recess 51 is preferably formed by using a cast casting surface that does not require machining, and is particularly smooth if the front housing 5 is a cast product such as an aluminum die cast in which an aluminum alloy is cast. The cast casting surface can be used as it is.

Furthermore, the thrust receiving portion 5C of the front housing 5 is machined into a substantially flat shape by machining, but by providing a smooth surface at the connecting portion between the recess 51 and the thrust receiving portion 5C in the casting stage. Thus, it becomes possible to eliminate the burr processing after processing.

Further, since the concave portion 51 having an arc shape with a radius R is provided, the arc shape can be used as an R shape for ensuring strength at the corner portion of the front housing 5. Such an R shape hardly affects the securing of the gap δ, which is advantageous for downsizing.
Further, the recess 51 is formed by radially providing a recessed groove portion serving as the communication passage 53 on the thrust receiving surface 5B, thereby providing a space between the space communicating with the suction port 45 and the narrow space where the crankshaft 11 and the like are disposed. Is preferably communicated. By providing this communication path 53, a part of the low-temperature and low-pressure refrigerant gas introduced from the suction port 45 is supplied into the narrow space through the communication path 53.

The scroll compressor configured as described above operates as follows.
When a rotational driving force is transmitted from an external driving source to the crankshaft 11 via a pulley, an electromagnetic clutch, etc. (not shown) and the crankshaft 11 is rotated, the eccentric pin 11C of the crankshaft 11 is connected to the eccentric pin 11C via the drive bush 19 and the drive bearing 21. The orbiting scroll member 27 coupled to the fixed scroll member 25 is driven to rotate orbit with respect to the fixed scroll member 25 while being prevented from rotating by the rotation preventing mechanism 33. As a result, the refrigerant gas in the suction chamber 43 is sucked into the three-month compression chamber 29 formed at two radially outermost positions. As described above, generally, the scroll compression mechanism 23 composed of the orbiting scroll member 27 and the fixed scroll member 25 has two suction ports at positions facing approximately 180 °. The space of the gap portion δ and the recess 51 formed between the inner surface of 5A and the scroll compression mechanism 23 passes from the suction port 45 provided in the housing 3 to two compression mechanism suction ports, that is, inside the compression chamber 29. It becomes a flow path for guiding the refrigerant gas.
The compression chamber 29 is moved to the center side while being reduced in volume after being closed by suction at a predetermined turning angle position. During this time, the refrigerant gas is compressed, and when the compression chamber 29 reaches a position where it communicates with the discharge port 25C, the discharge reed valve 37 is pushed open and the compressed gas is discharged into the discharge chamber 41. Then, it is discharged out of the scroll compressor 1.

  Thus, according to the present invention described above, the recess 51 is formed on the outer side of the thrust receiving surface 5B that supports the compression mechanism to secure the cross-sectional area of the gas fluid, so that the size of the gap δ is reduced. Thus, the diameter of the housing 3 can be reduced. Furthermore, in the present invention, by providing the arc-shaped concave portion 51 with the radius R, the external dimensions are reduced as much as the influence of the interference between the housing 3 and the orbiting scroll member 27 when the orbiting scroll member 27 is driven. There is also an advantage that downsizing becomes possible.

With respect to this point, the present invention will be described in detail with reference to FIG. 3A and the conventional example shown in FIG.
In the conventional example, δ _{0 is set} so as not to interfere with the outermost part when the orbiting scroll member 27 is driven.
Since the side wall root R for avoiding stress concentration on the side wall is provided while securing the gap, the outer diameter of the compressor has to be increased. By providing 51, δ ₀
In addition, the installation of R for securing the strength is possible on the inner side (center side) as long as the outer scroll does not interfere with the outermost end when the orbiting scroll is driven. In this case, the draft angle of the aluminum die-cast housing 3 is necessary as in the conventional case, but the rise of the side wall can be installed on the inner side, so the outer diameter of the compressor can be further reduced. It becomes.

Further, by providing the recess 51 in the present invention more deeply, it is possible to increase the volume inside the housing while maintaining the outer diameter. In this case, the muffler effect is exhibited and the compressor is used. It is possible to reduce the generated pulsation, which can contribute to low vibration and low noise.
In addition, although there is a concern about an increase in the dimension in the axial direction by providing the recess 51, it is common to have existing components such as bearings around the recess installation location, and in reality the axial length direction There is no increase.

Further, a technique is also known in which a separate plate or the like for preventing wear is provided between the thrust receiving portion 5C of the scroll compressor 1 and the orbiting scroll member 27. Needless to say, it is possible to achieve the same effect as.
In the above-described embodiment, the scroll compressor 1 has been described as an example. However, the present invention is not limited to this, and other examples such as a rotary compressor, a screw compressor, a swash plate compressor, and the like. It can be widely applied to fluid machines other than compressors such as similar type pumps as well as compressors of the type.

It is sectional drawing which shows the structural example of a scroll compressor as one Example of the fluid machine which concerns on this invention. It is AA sectional drawing of FIG. (A) is principal part sectional drawing to which the B section of FIG. 1 was expanded, (b) is principal part sectional drawing which shows the conventional structure of the part.

Explanation of symbols

1 Scroll compressor (fluid machine)
3 Housing 5 Front housing (low pressure side housing)
5A trunk (mouth wide part)
5B Thrust receiving surface 5C Thrust receiving part 5D, 5E Bearing housing part (narrow part)
5F Small diameter boss part (narrow part)
7 Rear housing (High-pressure side housing)
11 Crankshaft (compression mechanism drive)
23 Scroll compression mechanism 25 Fixed scroll member (compression mechanism body)
27 Orbiting scroll member (compression mechanism body)
51 Concavity 53 Communication path

Claims (6)

In a fluid machine in which a compression mechanism is housed and installed in a funnel-shaped housing, a compression mechanism main body of the compression mechanism is disposed in a wide portion of the housing, and a compression mechanism driving unit is disposed in a narrow portion.
A fluid machine, wherein a recess is formed outside a compression mechanism support surface that is positioned on a bottom surface of the wide portion and supports the compression mechanism.   The fluid machine according to claim 1, wherein the recess and the internal space of the narrow portion communicate with each other.   The fluid machine according to claim 1, wherein the concave portion has an arc shape.   The fluid machine according to claim 3, wherein the recess is formed by a cast casting surface.   The fluid machine according to any one of claims 1 to 4, wherein the compression mechanism is a scroll compression mechanism, and the compression mechanism support surface is a thrust receiving surface. A compression mechanism is housed and installed in a housing having a low-pressure side housing provided with a suction port in the shape of a funnel, the compression mechanism main body of the compression mechanism is disposed in the wide portion of the low-pressure side housing, and the compression mechanism drive unit In a fluid machine in which
A fluid machine, wherein a concave portion is formed outside a thrust receiving surface that is located on a bottom surface of the wide portion and supports the compression mechanism.

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