JP4531710B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor, and more particularly, to axial positioning of a main shaft or restriction of axial movement of the main shaft.

  As the main shaft support structure of the compressor, the main shaft is rotatably supported by a plurality of radial bearings (radial bearings provided on both sides of the main shaft extending direction), and the pressing force to one side due to the compression reaction force rotates, for example, integrally with the main shaft There is known a structure in which a thrust bearing provided between a rotor and a front housing is used.

  However, in a compressor having such a spindle support structure, if the compression reaction force at the start of the compressor or during low-load operation cannot be obtained sufficiently, the axial position of the spindle is not determined, and noise / The occurrence of vibration is a concern. For example, Patent Documents 1 and 2 are disclosed as prior arts for solving such problems (however, these are not techniques for positioning the spindle).

The technique described in Patent Document 1 has a configuration in which an inner ring of a ball bearing (radial bearing) is abutted against an end of a main shaft, and an outer ring is abutted against a valve plate via a spring to position the main shaft. The technique described in Patent Document 2 is a configuration using a thrust bearing instead of a ball bearing. Both documents have the same basic configuration for spindle positioning in the direction of the compression reaction force.
JP 2001-329952 A Japanese Patent Laid-Open No. 2002-5022

  However, in the configuration where the main shaft is positioned on the anti-compression reaction force side using the ball bearing, thrust bearing and spring as described above, the reaction force of the spring always acts on the main shaft, resulting in power loss. To do. In particular, in a clutchless compressor used in an air conditioner or the like, the main shaft is always rotated even when the air conditioner is in an off state, so that reduction of power loss remains as a problem.

  Accordingly, an object of the present invention is to provide an inexpensive compressor that simplifies the structure of positioning or movement restriction of the spindle, can reduce power loss as described above, and can suppress generation of noise and vibration. It is to provide.

In order to solve the above problems, a compressor according to the present invention includes a main shaft that is rotatably supported by a plurality of radial bearings, and a compressor that includes a thrust bearing between a rotor fixed to the main shaft and a front housing. The radial bearing on the side opposite to the front housing includes a flange portion that extends to a position facing the end surface portion of the main shaft itself and has an opening diameter smaller than the outer diameter of the radial bearing support portion of the main shaft, and the main shaft end surface portion and the flange The movement of the main shaft to the side opposite to the front housing is restricted by the surface of the portion facing the end surface portion of the main shaft.

  That is, the radial bearing on the side opposite to the front housing that supports the main shaft is provided with a flange portion that extends to a position facing the end surface portion of the main shaft and has an opening diameter smaller than the outer diameter of the radial bearing support portion of the main shaft. By moving the flange portion and the main shaft end surface portion in contact with each other or by forming a minute gap therebetween, the movement of the main shaft to the side opposite to the front housing is restricted (restricted) by the flange portion. .

  When the compressor is a capacity-controlled compressor, the opening diameter of the flange is set to a diameter that can function as an orifice between the pressure regulating chamber side and the suction pressure region side of the compressor. It is preferable. If comprised in this way, it will become unnecessary to provide the orifice of the same function separately, and the structure can be simplified.

  The restriction of the movement of the main shaft toward the front housing side is, for example, the state of the main shaft end surface portion on the anti-front housing side and the flange portion in a state where the main shaft is abutted against the thrust bearing side between the rotor and the front housing. This can be done by positioning the radial bearing so that the surface facing the end surface of the main shaft is in contact with or in a minute gap. That is, assuming that the main shaft is pressed against the thrust bearing by the compression reaction force as a reference position for restricting movement of the main shaft, when the compression reaction force is lost or when the compression reaction force cannot be obtained sufficiently The amount by which the main shaft can move from the reference position to the side opposite to the front housing (the amount by which the main shaft can move in the axial direction) is restricted by the contact between the flange portion and the end surface portion of the main shaft or the minute gap therebetween. In view of the object of the present invention, the restricted movable amount may be an amount that can suppress the generation of noise and vibration accompanying the axial movement of the main shaft.

  In the compressor according to the present invention, it is preferable that a friction coefficient reducing member is interposed between a main shaft end surface portion on the side opposite to the front housing and a surface of the flange portion facing the main shaft end surface portion. As a result, even in an operating state in which the spindle end surface portion and the flange portion of the radial bearing are in contact with each other, the power loss can be minimized by the friction coefficient reducing member. This friction coefficient reducing member can be composed of, for example, a solid lubricant applied (for example, applied) to the surface of the main shaft end surface or / and the flange portion facing the main shaft end surface.

  Further, in the compressor according to the present invention, a disk-like member fixed to the main shaft end surface portion side or the flange portion side between the main shaft end surface portion and a surface of the flange portion facing the main shaft end surface portion. It is also possible to adopt a configuration in which is interposed. In this way, even if it is difficult to treat the appropriate solid lubricant on the flange portion of the radial bearing, the appropriate solid lubricant can be processed on the disk-shaped member instead of the bearing flange portion. It becomes possible. The friction coefficient reducing member is, for example, a solid lubricant applied to (for example, applied to) the disk-like member or / and the spindle end surface portion, or the surface facing the spindle end surface portion of the disc-shaped member or / and the flange portion. It can consist of Further, the friction coefficient reducing member can be formed by manufacturing the disk-like member member itself with a material having self-lubricating properties.

  Further, in the compressor according to the present invention, the fluid flows on the main shaft end surface portion side on the side opposite to the front housing or on the opposite surface side of the flange portion to the main shaft end surface portion even when both are in contact with each other. It is preferable that a groove is provided. In a state where both are in close contact with each other, there is a possibility that the passage formed between them may be blocked, and even if it is intended to have the function of the above-mentioned orifice, or there is an orifice behind the radial bearing, Although there is a possibility that it cannot function normally, such a fear can be surely removed by providing the groove as described above.

Moreover, in the compressor which concerns on this invention, it is also possible to set it as the structure by which the said collar part is bend | folded in the direction which approaches a spindle end surface part in the axial direction of a spindle. By adopting such a configuration, it becomes possible to give the collar part a spring function using its own elasticity, and the spring function allows the main shaft to move to the front housing side to be moved to the front housing side. Since it can be pushed back, the amount of axial movement of the main shaft can be further reduced .

  Further, in the compressor according to the present invention, a configuration in which a slit for reducing the rigidity of the flange itself is provided in the flange can be adopted. By adopting such a configuration, it is possible to give the collar part a spring function that uses its own elasticity, as described above, and adjust the elasticity of the spring function to an appropriate strength. As a result, it is possible to set the force for pushing back the main shaft toward the front housing to an optimum force, and at the same time, it is possible to reduce the amount of axial movement of the main shaft.

  As described above, according to the compressor according to the present invention, the axial movement amount of the main shaft is set so that the end surface portion of the main shaft and the flange portion of the radial bearing are in contact with each other or become a minute gap. It is possible to suppress the generation of noise and vibration due to axial movement of the main shaft. Further, the spindle end surface portion and the flange portion of the radial bearing have a structure that is basically not in contact with each other, so that no power loss occurs between them. Even if the main shaft end face and the flange of the radial bearing come into contact with each other, the power loss can be minimized by interposing the friction coefficient reducing member. And since this invention can be implemented by providing the collar part of a predetermined structure in a radial bearing, it can be implemented cheaply with a simple structure.

Hereinafter, preferred embodiments of a compressor according to the present invention will be described with reference to the drawings.
First, an example of a compressor to which the present invention can be applied will be described with reference to FIG. 1 while referring to a conventional configuration and specifically referring to a compressor described in Patent Document 2 described above. FIG. 1 shows a capacity-controlled swash plate compressor 1, which includes a main shaft 4 that is rotatably supported by a plurality of radial bearings 2 and 3, and a rotor 5 fixed to the main shaft 4. A thrust bearing 7 is provided between the front housing 6 and the thrust bearing 7 receives most of the compression reaction force. Since the main shaft 4 is rotatably supported by the radial bearings 2 and 3 on both sides, there is a possibility that the main shaft 4 moves in the axial direction when the compression reaction force is not sufficient as described above. This axial movement is prevented or suppressed by a spring 8 provided in the vicinity of the radial bearing 3 on the side opposite to the front housing 6. However, in this structure, the power loss is large because the spring force always acts as described above. In FIG. 1, 9 is a swash plate, 10 is a rotor side connecting portion, 11 is a swash plate side arm, 12 is a piston reciprocally inserted in a cylinder bore 14 formed in the cylinder block 13, and 15 is a piston. 12 is a shoe for slidingly engaging the swash plate 9, 16 is a crank chamber, 17 is a suction chamber formed in the cylinder head 18, 19 is a discharge chamber, 20 is a valve plate, 21 is a suction chamber 17 and a cylinder bore 14 , 22 is a discharge hole, and 23 is a capacity control valve.

  In the present invention, the radial bearing portion on the side opposite to the front housing is configured as follows without providing the spring 8 with respect to the compressor having the above structure.

FIG. 2 shows a structure according to the first embodiment of the present invention. In FIG. 2, reference numeral 31 denotes a main shaft, and the end portion on the side opposite to the front housing of the main shaft 31 is rotatably supported by a radial bearing 33 fitted in the cylinder block 32. The radial bearing 33 includes a flange portion 36 that extends to a position facing the end surface portion 34 of the main shaft itself and has an opening diameter (35 is an opening portion) that is smaller than the outer diameter of the radial bearing support portion of the main shaft 31. A minute gap 37 is formed between the main shaft end surface portion 34 and the flange portion 36, and the anti-front housing of the main shaft 31 is formed by the main shaft end surface portion 34 and the surface of the flange portion 36 facing the main shaft end surface portion 34. Movement to the side (to the right in FIG. 2) is restricted.

  For example, when the compression reaction force is not sufficient, when the main shaft 31 attempts to move in the axial direction (to the right side in FIG. 2), the main shaft end surface portion 34 abuts against the flange portion 36, thereby further restricting the movement. The Therefore, the movable amount of the main shaft 31 is suppressed to be minute, and the generation of noise and vibration accompanying the movement of the main shaft 31 is suppressed.

  In the above structure, since the main shaft end surface portion 34 and the flange portion 36 are basically kept in a non-contact state in normal times, no power loss occurs in this portion. In order to minimize the power loss at that time in consideration of the case where the two come into contact with each other, for example, solid lubrication as a friction coefficient reducing member is provided on one of the opposing surfaces of the spindle end surface portion 34 and the flange portion 36. What is necessary is just to apply the agent.

  FIG. 3 shows a structure according to Embodiment 2 of the present invention. In the structure shown in FIG. 3, a disk-shaped member 43 is interposed between the spindle end surface portion 34 and the flange portion 42 of the radial bearing 41. In this embodiment, the disk-shaped member 43 is located on the side of the spindle end surface portion 34. It is fixed by being press-fitted into the boss hole. A minute gap 37 is formed between the disk-shaped member 43 and the flange portion 42, and the anti-front housing of the main shaft 31 is formed by the disk-shaped member 43 and the surface of the flange portion 42 facing the disk-shaped member 43. Movement to the side (to the right in FIG. 3) is restricted. Also, in consideration of the case where both come into contact, in order to minimize the power loss at that time, for example, a solid lubricant is applied to one of the opposing surfaces of the disk-like member 43 and the flange portion 42. It is preferable to keep it.

  Even in such a configuration, when the compression reaction force is not sufficient, when the main shaft 31 tries to move in the axial direction (to the right side in FIG. 3), the disk-like member 43 fixed to the main shaft end surface portion 34 has the flange portion. Further contact with 42 is limited. Therefore, the movable amount of the main shaft 31 is suppressed to be minute, and the generation of noise and vibration accompanying the movement of the main shaft 31 is suppressed. In addition, since the wearable portion due to the contact between the opposing surfaces can be carried by the disk-like member 43 that is basically irrelevant to the function of the compressor, no problem occurs even if the opposing surfaces contact each other. .

  FIG. 4 shows a structure according to Embodiment 3 of the present invention. In the structure shown in FIG. 4, the flange portion 51 of the radial bearing 41 is bent toward the disk-like member 43 side fixed to the spindle end surface portion 34 side, as compared with the structure shown in FIG. 3. The front end portion of the bent collar portion 51 is in contact with the disk-like member 43, and the above-described minute gap 37 is not formed. Since the minute gap is not formed from the beginning, the axial movement of the main shaft 31 is further suppressed. Moreover, the bending structure of the collar part 51 makes it possible to exert the elasticity of the collar part 51 itself, and it is possible to apply a force to push back the main shaft 31 used for movement in the axial direction. .

  FIG. 5 shows a structure according to Embodiment 4 of the present invention. In the structure shown in FIG. 5, the disc-like member 61 is fixed to the flange 51 side of the radial bearing 41 as compared to the structure shown in FIG. 4. Also in this case, the same operation and effect as the third embodiment shown in FIG. 4 can be obtained. However, in the case of applying the solid lubricant, it is applied to the facing surface of either the spindle end surface portion 34 or the disk-shaped member 61.

  FIG. 6 shows a case where, for example, a plurality of slits 71 extending in the radial direction are provided in the flange portion 51 of the third embodiment or the fourth embodiment. By providing such a slit 71, the rigidity of the collar part 51 itself can be moderately weakened, and the elasticity of the collar part 51 can be exhibited more appropriately.

  FIG. 7 shows a case where, for example, a groove 81 extending in the radial direction is provided in the main shaft end surface portion 34 of the first embodiment or the fourth embodiment. By providing such a groove 81, it is possible to always ensure a fluid passage even when the spindle end surface portion 34 and the flange portion are in contact with each other. Therefore, when the opening diameter of the flange portion is set to a diameter that can function as an orifice between the pressure regulating chamber side and the suction pressure region side of the compressor, the function of the orifice can be secured constantly. become.

  As described above, in the structures of the first and second embodiments, the generation of noise and vibration accompanying the axial movement of the main shaft is appropriately suppressed by setting the gap between the main shaft end surface and the flange portion of the radial bearing. Further, in the structures of the third and fourth embodiments, it is not necessary to set a minute gap, so that the assembly is easy and the axial movement of the main shaft is suppressed more minutely. On the other hand, although there is a concern about power loss due to contact between the end face side of the main shaft and the flange side of the radial bearing, the power is reduced by the effect of reducing the pressing force due to the slit formation as shown in FIG. Loss can be suppressed to an acceptable level.

  The present invention is applicable to any compressor in which the main shaft is rotationally supported by a plurality of radial bearings.

It is a longitudinal cross-sectional view which shows an example of the conventional compressor. It is a schematic sectional drawing which shows the structure of the main-shaft end surface part and radial bearing part of the compressor which concerns on Example 1 of this invention. It is a schematic sectional drawing which shows the structure of the spindle end surface part and radial bearing part of the compressor which concerns on Example 2 of this invention. It is a schematic sectional drawing which shows the structure before (A) of a spindle end surface part and radial bearing part of a compressor concerning Example 3 of the present invention, and after assembly (B). It is a schematic sectional drawing which shows the structure before (A) of a main shaft end surface part and radial bearing part of a compressor concerning Example 4 of the present invention, and after assembly (B). It is a front view of the collar part which shows the example of slit formation. It is a front view of the main-axis end surface part which shows the example of groove formation.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2, 3 Radial bearing 4 Main shaft 5 Rotor 6 Front housing 7 Thrust bearing 31 Main shaft 32 Cylinder block 33 Radial bearing 34 Main shaft end surface portion 35 Opening portion 36 鍔 portion 37 Minute clearance 41 Radial bearing 42 鍔 portion 43 Disk-like member 51 Bent collar 61 Disc-shaped member 71 Slit 81 Groove

Claims (12)

In a compressor having a main shaft that is rotatably supported by a plurality of radial bearings and a thrust bearing between a rotor fixed to the main shaft and a front housing, the radial bearing on the side opposite to the front housing is located on the end surface of the main shaft itself. A flange portion extending to an opposing position and having an opening diameter smaller than the outer diameter of the radial bearing support portion of the main shaft, and the main shaft end surface portion and the surface of the flange portion facing the main shaft end surface portion are opposite to the main shaft. A compressor characterized in that movement to the front housing side is restricted.   It is composed of a capacity-controlled compressor, and the opening diameter of the flange is set to a diameter that can function as an orifice between the pressure regulating chamber side and the suction pressure region side of the compressor. Item 2. The compressor according to Item 1.   The movement of the main shaft to the side opposite to the front housing is controlled in such a manner that the main shaft is abutted against the thrust bearing between the rotor and the front housing, and the main shaft end surface portion on the side opposite to the front housing and the main shaft on the flange portion. The compressor according to claim 1, wherein the radial bearing is positioned so that the surface facing the end surface is in contact with or in a minute gap.   The friction coefficient reducing member is interposed between a main shaft end surface portion on the side opposite to the front housing and a surface of the flange portion facing the main shaft end surface portion. Compressor.   5. The compressor according to claim 4, wherein the friction coefficient reducing member is made of a solid lubricant applied to a surface of the main shaft end surface portion and / or the flange portion facing the main shaft end surface portion.   A disc-like member fixed to the spindle end surface portion side or the flange portion side is interposed between the spindle end surface portion and the surface of the flange facing the spindle end surface portion. The compressor according to claim 1 or 2.   The compression according to claim 6, wherein a friction coefficient reducing member is interposed between the disk-shaped member and a surface of the flange portion facing the spindle end surface portion or the spindle end surface portion. Machine.   The friction coefficient reducing member is made of a solid lubricant applied to a surface of the disk-shaped member or / and the flange portion facing the main shaft end surface portion, or the disk-shaped member or / and the main shaft end surface portion. The compressor according to claim 7, wherein:   The compressor according to claim 7, wherein the friction coefficient reducing member is configured by manufacturing the disk-like member member itself from a material having self-lubricating properties.   A groove is provided on the side of the main shaft end surface on the side opposite to the front housing or on the side of the flange facing the main shaft end surface so that fluid can flow even when they are in contact with each other. The compressor according to any one of claims 1 to 9. The compressor according to any one of claims 1 to 10, wherein the flange portion is bent in the axial direction of the main shaft in a direction approaching the main shaft end surface portion.   The compressor according to any one of claims 1 to 11, wherein a slit for reducing the rigidity of the flange itself is provided in the flange.

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