JP2006183461A - Fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid machine which can effectively prevent poor lubrication in the sliding part of a rotary shaft. <P>SOLUTION: The fluid machine 1 is a fluid machine which effects lubrication of a constitution element by gas containing lubrication oil and consists of a housing 2; a rotary shaft 61; and a main bearing 62 situated in the housing 2 and supporting the rotary shaft 61. And, a space in the housing 2 is divided by the main bearing 62. Further, the rotary shaft 61 has a gas passage R through which divided spaces 21 and T in the housing 2 are intercommunicated. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a fluid machine, and more particularly to a fluid machine that can effectively prevent poor lubrication in a sliding portion of a rotating shaft.

  In a fluid machine, for example, a scroll compressor, a rotating shaft is supported by a bearing (main bearing), and the inside of the front case is blocked by this bearing to form a closed space (closed space). In such a configuration, when the fluid machine employs a gas mist lubrication method, it is difficult to supply gas into the front case (the front side of the rotating shaft). Then, there is a problem that poor lubrication occurs in the shaft seal portion (sliding portion) of the rotating shaft.

  In this problem, a technique described in Patent Document 1 is known for a conventional fluid machine (scroll type compressor). In a conventional fluid machine, a fixed scroll and a movable scroll (orbiting scroll) are accommodated in a housing, and a large-diameter portion of a rotating shaft is supported on a front side of the housing (within a front case) via a radial bearing. The conventional fluid machine revolves the movable scroll while preventing rotation about its own axis by rotation of the rotating shaft, and sucks gas from the suction chamber into the compression chamber formed by both scrolls. The gas is compressed while reducing the volume, and the gas is discharged into the discharge chamber.

  Here, in the conventional fluid machine, the front side end surface of the outer race of the radial bearing is brought into contact with the inner wall surface of the front housing (front case), and the front side end surface of the inner race and the inner wall surface of the front housing are brought close to each other. Create a space. Further, the conventional fluid machine has a locking portion for locking the rear side end portion of the shaft seal fitted between the outer peripheral surface of the small diameter portion of the rotating shaft and the center hole of the front housing. It is provided at the end edge, and the engaging part is close to the large diameter part of the rotating shaft. Further, the conventional fluid machine is provided with a lubricating means for lubricating the radial bearing and the shaft seal portion with respect to at least one member of the front housing, the radial bearing and the rotating shaft.

  In the conventional fluid machine, such a configuration prevents poor lubrication in the sliding portion of the rotating shaft.

JP 7-253088 A

  An object of this invention is to provide the fluid machine which can prevent the lubrication failure in the sliding part of a rotating shaft effectively.

  In order to achieve the above object, a fluid machine according to the present invention is a fluid machine that lubricates components with a gas containing lubricating oil, and is arranged in the housing, a rotating shaft, and the housing. And a main bearing that supports the shaft, the space in the housing is divided by the main bearing, and the rotating shaft has a gas passage that communicates both the spaces in the divided housing. It is characterized by.

  In this fluid machine, a gas passage is formed in the rotating shaft, and both spaces in the housing divided by the main bearing are communicated with each other through the gas passage. As a result, gas can be circulated between the two separated spaces, and there is an advantage that poor lubrication in the sliding portion of the rotating shaft is effectively suppressed.

  Further, in the fluid machine according to the present invention, the gas passage is formed at a position deviating from a line of reaction force of the reaction force from the main bearing in a radial sectional view of the rotating shaft.

  In this fluid machine, the gas passage of the rotating shaft is formed at a position deviated from the reaction line of the reaction force from the main bearing in the radial sectional view of the rotation shaft. There is an advantage that the strength of the rotating shaft is maintained as compared with the configuration in which the is formed.

  In the fluid machine according to the present invention, the gas passage is constituted by a recess formed on a side surface of the rotating shaft.

  In this fluid machine, a concave portion is formed on the side surface of the rotating shaft, and the gas passage of the rotating shaft is formed by the concave portion, so that there is an advantage that the gas passage can be easily formed.

  In the fluid machine according to the present invention, the recess is formed in a plane with respect to the rotation axis.

  In this fluid machine, since the concave portion serving as the gas passage is formed in a plane with respect to the rotation axis, there is an advantage that the processing is easy.

  In the fluid machine according to the present invention, the fitting portion between the rotating shaft and the main bearing is constituted by an annular member having a peripheral surface attached to the shaft main body of the rotating shaft.

  In this fluid machine, an annular member is attached to the shaft main body of the rotating shaft, and the annular member constitutes the peripheral surface of the fitting portion. Therefore, the annular member functions as an inner race of the main bearing and rotates. There is an advantage that the rotation of the shaft is smoothed.

  In the fluid machine according to the present invention, the annular member and the shaft main body of the rotating shaft are made of materials having different material strengths.

  In this fluid machine, the annular member and the shaft body of the rotary shaft are made of materials having different material strengths. Therefore, for example, the annular member has a strength (hardness or rigidity) that can suppress wear due to friction with the main bearing, and the shaft body has a hardness (e.g., the recess (gas passage R) can be easily processed). A structure having processability) is possible. Thereby, there exists an advantage which can optimize the structure of a rotating shaft.

  In the fluid machine according to the present invention, the end of the concave portion is formed in an R shape in a radial cross-sectional view of the fitting portion with the main bearing.

  In this fluid machine, since the end of the concave portion is formed in an R shape in a radial sectional view of the fitting portion with the main bearing, stress concentration at the end portion of the contact surface between the rotating shaft and the annular member is alleviated. There are advantages.

  In the fluid machine according to the present invention, the rotating shaft has a reinforcing portion that reinforces a portion where the gas passage is formed.

  In this fluid machine, since the reinforcing portion is provided in the portion where the gas passage of the rotating shaft is formed, there is an advantage that the bending of the rotating shaft due to the load is reduced.

  In the fluid machine according to the present invention, a gas passage is formed in the rotating shaft, and both spaces in the housing separated by the main bearing are communicated with each other through the gas passage. Gas can be distributed between them, and there is an advantage that poor lubrication in the sliding portion of the rotating shaft is effectively suppressed.

  Hereinafter, the present invention will be described in detail with reference to the drawings. Note that the present invention is not limited to the embodiments. The constituent elements of this embodiment include those that can be easily replaced by those skilled in the art or those that are substantially the same. In addition, a plurality of modifications described in this embodiment can be arbitrarily combined within a range obvious to those skilled in the art.

  1 is a cross-sectional view showing a fluid machine according to Embodiment 1 of the present invention. 2 and 3 are an explanatory view (FIG. 2) and a radial cross-sectional view (FIG. 3) showing a rotating shaft of the fluid machine shown in FIG. 4-7 is explanatory drawing which shows the modification of the rotating shaft described in FIG.

[Fluid machine]
In the first embodiment, a scroll compressor of a vehicle air conditioner will be described as an example of the fluid machine 1. The fluid machine 1 has a function of compressing gas (refrigerant) and supplying it to a refrigerant circuit of a vehicle air conditioner. In the fluid machine 1, each part (between the scrolls 4 and 5 and the sliding part of the intermediate mechanism 7) is lubricated by mist-like lubricating oil contained in the gas. The fluid machine 1 includes a housing 2, a fixed scroll 4, a turning scroll 5, a drive mechanism 6, and an intermediate mechanism 7.

  The housing 2 includes a housing body 2A and a front case 2B. The housing body 2A is made of a container-shaped member, and has a suction chamber 21 and a discharge chamber 22 therein. Further, the housing body 2A has a suction port 23 and a discharge port (not shown) on its side. The front case 2B is a case that houses the drive mechanism 6, and is attached to the opening of the housing body 2A to seal the inside of the housing body 2A. The front case 2B is bolted (not shown) to the housing body 2A. In the fluid machine 1, external gas is taken into the suction chamber 21 in the housing 2 from the suction port 23, and gas in the discharge chamber 22 is discharged to the outside from the discharge port.

  The fixed scroll 4 has an end plate portion and a spiral wrap portion formed on the end plate portion. The fixed scroll is accommodated in the housing 2 (housing main body 2A) with the lap portion facing the suction chamber 21, and is fixed to the inner wall surface of the housing 2 at the end plate portion. Further, the fixed scroll 4 (end plate portion) also serves as a partition member that partitions the suction chamber 21 and the discharge chamber 22 in the housing 2.

  The orbiting scroll 5 has an end plate portion and a spiral wrap portion formed on the end plate portion. The orbiting scroll 5 is installed in the housing 2 (housing main body 2 </ b> A) so that the lap portion meshes with the wrap portion of the fixed scroll 4 while being eccentric. With such an arrangement, a plurality of sealed spaces S are formed between the wrap portions of the fixed scroll 4 and the orbiting scroll 5. Further, the orbiting scroll 5 is disposed so as to be able to perform a revolving orbiting motion while preventing rotation with respect to the fixed scroll 4. In addition, the orbiting scroll 5 and the fixed scroll 4 are arranged so that the volume of the sealed space S is gradually reduced by the revolution orbiting motion of the orbiting scroll 5.

  The drive mechanism 6 includes a rotating shaft 61, a main bearing 62, a sub bearing 65, and a pulley 63. The rotary shaft 61 is a drive shaft for driving the orbiting scroll 5. The rotating shaft 61 is fixed to the pulley 63 at one end, and is connected to the intermediate mechanism 7 at the other end. The main bearing 62 and the sub bearing 65 are bearings for supporting the rotating shaft 61 and are disposed in the front case 2B (housing 2). The pulley 63 is rotatably installed on the outer periphery of the front case 2B. The pulley 63 is connected to an external power source (vehicle engine) via a drive belt (not shown).

  The intermediate mechanism 7 is a mechanism that connects the rotating shaft 61 of the drive mechanism 6 and the orbiting scroll 5 and is configured by, for example, an Oldham mechanism. The intermediate mechanism 7 has a function of converting the rotary motion of the rotary shaft 61 into a revolving orbiting motion and transmitting it to the orbiting scroll 5.

  In the fluid machine 1, first, when power is transmitted to the pulley 63 of the drive mechanism 6, the rotating shaft 61 rotates together with the pulley 63. Then, the rotary motion of the rotary shaft 61 is transmitted to the orbiting scroll 5 via the intermediate mechanism 7, and the orbiting scroll 5 performs a revolving orbiting motion with respect to the fixed scroll 4. Then, the gas in the suction chamber 21 is taken from the surroundings into the sealed space S between the orbiting scroll 5 and the fixed scroll 4, and the gas in the sealed space S is compressed by narrowing the sealed space S. Then, the compressed gas is discharged from a hole 41 formed substantially at the center of the fixed scroll 4, flows into the discharge chamber 22, is discharged from the discharge port, and is supplied to the outside.

[Gas passage]
In the fluid machine 1, the hollow portion 25 is formed in the front case 2 </ b> B of the housing 2, and the rotary shaft 61 of the drive mechanism 6 is inserted into the hollow portion 25 (see FIGS. 1 and 2). ). Further, the rotating shaft 61 has a fitting portion 611 formed with a large diameter, and is fitted to the main bearing 62 by the fitting portion 611. Moreover, the main bearing 62 is comprised by the radial bearing, for example, and is arrange | positioned at the inner side opening part (opening part by the side of the intermediate mechanism 7) of the hollow part 25, and supports the rotating shaft 61. FIG. For this reason, in this fluid machine 1, the hollow portion 25 of the front case 2B is blocked by the main bearing 62 at its inner opening and is substantially closed.

  On the other hand, a shaft seal 64 is fitted on the rotary shaft 61. The shaft seal 64 is located at the outer opening of the hollow portion 25 (opening on the pulley 63 side), and seals the gap between the rotating shaft 61 and the inner periphery of the hollow portion 25 at this position. Therefore, in the fluid machine 1, the closed space T closed in the hollow portion 25 is formed by arranging the main bearing 62 and the shaft seal 64.

  A gas passage R is formed in the rotating shaft 61 (see FIGS. 2 and 3). This gas passage R is a passage for supplying the gas on the suction chamber 21 side containing the lubricating oil to the closed space T in the front case 2B. The gas passage R is formed in the fitting portion 611 of the rotating shaft 61, and communicates the suction chamber 21 side and the closed space T in a state where the fitting portion 611 is fitted to the main bearing 62.

  In such a configuration, the gas containing lubricating oil flows into the closed space T from the suction chamber 21 side through the gas passage R of the fitting portion 611 (see FIG. 2). As a result, the gas circulates in the closed space T, and the sliding portion (the shaft seal 64 and the like) of the rotating shaft 61 is lubricated.

[effect]
In the fluid machine 1, a gas passage R is formed in the rotating shaft 61 (the fitting portion 611 thereof), and both spaces (suction chambers) in the housing 2 separated by the main bearing 62 through the gas passage R. The space on the 21 side and the closed space T) are in communication (see FIG. 2). As a result, gas can be circulated between the suction chamber 21 side and the closed space T, and therefore, there is an advantage that the poor lubrication in the sliding portion (particularly the shaft seal 64) of the rotating shaft 61 is effectively suppressed. .

  In the fluid machine 1, since the gas passage R is formed in the rotating shaft 61, the rotating shaft 61 is reduced in weight compared to a configuration in which the gas passage R is not formed in the rotating shaft 61. This has the advantage that the cost of the product can be reduced.

  Further, when the fluid machine 1 is in operation, a load from the orbiting scroll 5 is applied to the rotating shaft 61, and the fitting portion 611 of the rotating shaft 61 receives a reaction force from the main bearing 62 due to this load. Here, the reaction force acts on the rotating shaft 61 from a certain direction because the load from the orbiting scroll 5 moves as the rotating shaft 61 rotates. In this respect, in this fluid machine 1, the gas passage R of the rotary shaft 61 is formed at a position deviated from the action line l from the orbiting scroll 5 in the radial sectional view of the fitting portion 611 of the rotary shaft 61. (See FIG. 4). In other words, the gas passage R of the rotating shaft 61 is formed at a position off the action line l of the reaction force acting on the rotating shaft 61 from the main bearing 62. Thereby, compared with the structure in which the gas passage R is formed on the line of action l of the load from the orbiting scroll 5, there is an advantage that the strength of the rotating shaft 61 against the load (reaction force) is maintained.

  Moreover, in this fluid machine 1, the fitting part 611 of the rotating shaft 61 is comprised by the shaft main body 612 and the annular member 613 (refer FIG. 3). A recess is formed in the outer peripheral surface of the shaft body 612, and the gas passage R of the rotating shaft 61 is configured by this recess. The shaft main body 612 has a cross-sectional shape in which circular both side portions are cut away in the radial cross-sectional view of the fitting portion 611 of the rotating shaft 61 due to the recess (gas passage R). In such a configuration, since the gas passage R of the rotating shaft 61 is configured by the recess formed in the outer peripheral surface of the shaft body 612, there is an advantage that the gas passage R can be easily formed.

  In the fluid machine 1, the annular member 613 is attached to the shaft main body 612 of the rotating shaft 61, and the circumferential surface of the fitting portion 611 is configured by the annular member 613. The annular member 613 is, for example, a cylindrical tube, and is attached to a position on the outer periphery of the shaft main body 612 where a recess is formed. Further, the shaft body 612 is press-fitted into the annular member 613, whereby the annular member 613 is fixed to the shaft body 612. In such a configuration, since the annular member 613 functions as an inner race of the main bearing 62, there is an advantage that the rotation of the rotating shaft 61 is smoothed.

  Further, in the fluid machine 1, the fitting portion 611 of the rotating shaft 61 is configured by the shaft main body 612 and the annular member 613, and the shaft main body 612 and the annular member 613 are configured by separate members (see FIG. 3). . In such a configuration, the outer periphery (annular member 613) of the fitting portion 611 can have different strengths with respect to the shaft main body 612. Thereby, there exists an advantage which can optimize the structure of a rotating shaft. Specifically, a configuration in which the annular member 613 has higher strength than the shaft main body 612 is possible. In addition, the annular member 613 preferably has a strength (hardness or rigidity) to the extent that wear due to friction with the main bearing 62 is suppressed. On the other hand, it is preferable that the shaft body 612 has a hardness (easiness of processing) to such an extent that the recess (gas passage R) can be easily processed. With such a configuration, there is an advantage that the workability of the shaft main body 612 (the recess that is the gas passage R) can be ensured while ensuring the wear resistance of the fitting portion 611. Further, since the shaft body 612 having low rigidity can be adopted, there is an advantage that the cost of the product can be reduced. Such a configuration includes a configuration in which the annular member 613 is made of a material having higher rigidity than the shaft body 612 and a configuration in which heat treatment is performed on the outer periphery of the annular member 613.

  Moreover, in this fluid machine 1, the reinforcement part 614 which reinforces the part (fitting part 611) in which the gas path R is formed among the parts of the rotating shaft 61 is formed (refer FIG. 3). The reinforcing portion 614 is, for example, a rib formed in the axial direction of the rotating shaft 61 with respect to the fitting portion 611, and reinforces the strength of the rotating shaft 61 in the step portion of the fitting portion 611. Thereby, there exists an advantage by which the bending of the rotating shaft 61 by a load is reduced. In this configuration, when the fitting portion 611 of the rotating shaft 61 is configured by the shaft main body 612 and the annular member 613, the reinforcing portion 614 is formed with respect to the shaft main body 612. Accordingly, there is an advantage that necessary strength can be imparted to the shaft body 612 when the shaft body 612 is made of a low-strength material for processing the recess.

[Modification 1]
In the fluid machine 1, the fitting portion 611 includes a shaft main body 612 having a recess, and an annular member 613 that is attached to the outer periphery of the shaft main body 612 and forms the outer periphery of the fitting portion 611. The gas passage R is constituted by the recesses (see FIG. 3). Here, the recess (gas passage R) of the shaft body 612 is preferably formed to be planar with respect to the side surface of the shaft body 612. That is, it is preferable that the recess of the shaft main body 612 is formed with a straight line when the fitting portion 611 is viewed in a radial cross section (see FIG. 4). Such a configuration has an advantage that the recess can be easily processed.

[Modification 2]
In addition, the shaft body 612 preferably has an R shape at the end (end of the recess) in the radial sectional view of the fitting portion 611 (see FIG. 5). In such a configuration, the stress concentration at the end of the contact surface between the shaft main body 612 and the annular member 613 is relieved by the R shape of the recess. Thereby, there exists an advantage by which the damage of an edge part is prevented.

[Modification 3]
Further, in the fluid machine 1, the gas passage R of the rotating shaft 61 is configured by a recess formed in the outer peripheral surface of the shaft body 612 (see FIG. 3). However, the present invention is not limited thereto, and the gas passage R of the rotating shaft 61 may be configured by a through hole formed in the rotating shaft 61 (see FIG. 6). That is, a through hole is formed in the axial direction of the rotating shaft with respect to the fitting portion 611 of the rotating shaft 61, and in the installed state of the rotating shaft 61, the through holes are formed on both sides of the main bearing 62 (on the suction chamber 21 side). The closed space T side) may be communicated. In such a configuration, gas flows between the suction chamber 21 side and the closed space T side through the through hole (gas passage R) of the rotating shaft 61. Thereby, there exists an advantage by which the poor lubrication in the sliding part of the rotating shaft 61 is suppressed effectively.

[Modification 4]
In the fluid machine 1, the outer peripheral surface of the fitting portion 611 is configured by the annular member 613 attached to the shaft body 612. However, the present invention is not limited to this, and the annular member 613 may be omitted (see FIG. 7). Thereby, there exists an advantage by which the number of parts of the rotating shaft 61 is reduced.

[Modification 5]
Further, in the fluid machine 1, the sectional area of the gas passage R is approximately 30 [%] with respect to the total sectional area of the fitting part 611 (including the annular member 613) in the radial sectional view of the fitting part 611. The following is more preferable. Thereby, there exists an advantage that the rigidity of a rotating shaft is ensured and the flow-path cross-sectional area of gas is ensured.

[Application example]
In this embodiment, the scroll compressor of the vehicle air conditioner has been described as an example of the fluid machine 1. However, the present invention is not limited to this, and the fluid machine 1 may be applied to a compressor of another air conditioner having a shaft seal. For example, the fluid machine 1 may be applied to a scroll compressor for a stationary gas heat pump. May be.

  As described above, the fluid mechanical point according to the present invention is useful in that it can effectively prevent poor lubrication in the sliding portion of the rotating shaft.

It is sectional drawing which shows the fluid machine concerning the Example of this invention. It is explanatory drawing which shows the rotating shaft of the fluid machine described in FIG. It is radial direction sectional drawing which shows the rotating shaft of the fluid machine described in FIG. It is explanatory drawing which shows the modification of the rotating shaft described in FIG. It is explanatory drawing which shows the modification of the rotating shaft described in FIG. It is explanatory drawing which shows the modification of the rotating shaft described in FIG. It is explanatory drawing which shows the modification of the rotating shaft described in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Fluid machine 2 Housing 2A Housing main body 2B Front case 21 Suction chamber 22 Discharge chamber 23 Suction port 25 Hollow part 4 Fixed scroll 41 Hole 5 Orbiting scroll 6 Drive mechanism 61 Rotating shaft 611 Fitting part 612 Shaft part 613 Annular member 614 Rib 62 Main bearing 63 Pulley 64 Shaft seal 7 Intermediate mechanism R Gas passage S Sealed space T Closed space

Claims (8)

A fluid machine that lubricates components with a gas containing lubricating oil,
A housing, a rotating shaft, and a main bearing disposed in the housing and supporting the rotating shaft, wherein the space in the housing is divided by the main bearing, and the rotating shaft is divided A fluid machine having a gas passage for communicating both spaces in the housing.   2. The fluid machine according to claim 1, wherein the gas passage is formed at a position deviating from a line of reaction of a reaction force from the main bearing in a radial sectional view of the rotating shaft.   The fluid device according to claim 1, wherein the gas passage is configured by a recess formed in a side surface of the rotating shaft.   The fluid machine according to claim 3, wherein the recess is formed in a plane with respect to the rotation axis.   The fitting part of the said rotating shaft and the said main bearing is comprised by the cyclic | annular member with which the surrounding surface was mounted | worn with the shaft main body of the said rotating shaft. The fluid machine described.   The fluid machine according to claim 5, wherein the annular member and the shaft main body of the rotating shaft are made of materials having different material strengths.   The fluid machine according to claim 5 or 6, wherein an end of the concave portion is formed in an R shape in a radial cross-sectional view of a fitting portion with the main bearing.   The fluid machine according to claim 1, wherein the rotating shaft has a reinforcing portion that reinforces a portion where the gas passage is formed.

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