JP3196645U - Mechanical seal device - Google Patents

Abstract

An object of the present invention is to provide a mechanical seal device that can realize energy saving while maintaining good sealing performance, can be manufactured by a simple operation, and can reduce manufacturing costs. A mechanical seal device 1 rotates with a maining ring 20 provided on a housing 60 side and a shaft member 50, and is slid against an end surface of the maining ring by being urged in an axial direction by a spring. And a seal ring 10 having a moving surface. The maining ring has a convex portion 20A which is provided on the surface facing the seal ring and whose radial dimension W3 is narrower than the radial dimension W4 of the mainting ring, and the axial end surface 20c of the convex portion 20A. However, it slides with the axial end surface 10b of the convex portion 10A of the seal ring. [Selection] Figure 2

Description

  The present invention relates to a mechanical seal device used in the general industrial equipment (GI) field, and more particularly to a mechanical seal device applied to a pump device such as a submersible pump or a general land pump.

  Conventionally, the structure which made the sliding surface of a maining ring and a seal ring small from the viewpoint of the energy-saving requested | required of a mechanical seal apparatus is employ | adopted. Specifically, as shown in FIGS. 5A and 5B, in the mechanical seal device 100 attached to the shaft member 200, the width of the seal ring 110 on the maining ring side is narrowed in the radial direction. By providing the convex portion 110A, the sliding area between the axial seal ring side end surface 110a of the convex portion 110A and the maining seal side end surface 120a of the mainting ring 20 is reduced. As a result, the non-sliding area that does not slide with the maining ring 120 can be increased at the end of the seal ring 110 on the side of the maining ring, and the sliding area can be secured while ensuring the inherent sealing performance of the mechanical seal device. It is possible to realize energy saving by reducing the size of the system.

  In the mechanical seal device configured as described above, from the viewpoint of further energy saving, in recent years, there are maining rings formed of hard materials such as alumina ceramics and SiC having a low friction coefficient. However, with the conventional surface processing method, even if there is a non-sliding surface that does not slide with the seal ring on the end surface on the axial seal ring side of the maining ring, the entire surface on the seal ring side of the maining ring Therefore, it is necessary to perform processing with high precision such as surface roughness and flatness, and the processing cost of the sliding surface accounts for a large proportion of the total processing cost of the mechanical seal device. For this reason, the processing work is complicated and cost disadvantages occur. In particular, when the maining ring is mass-produced with the hard material as described above, such a problem becomes remarkable. Further, it is possible to reduce the outer diameter of the maining ring and reduce the area of the end face on the axial seal ring side in advance before the above processing, but change the mold for molding the maining ring, Furthermore, it is necessary to change the mold for molding the gasket for fixing the maining ring to the housing, which increases the manufacturing cost.

  An object of the present invention is to provide a mechanical seal device that can realize energy saving while maintaining good sealing performance, can be manufactured by a simple operation, and can reduce manufacturing costs. is there.

In order to achieve the above object, a mechanical seal device of the present invention is a mechanical seal that seals between a housing and a shaft member, and a stationary ring provided on the housing side,
A rotating ring having a sliding surface that rotates together with the shaft member and is urged in an axial direction by an urging member and slides against an end surface of the fixed ring, and the rotating ring is A first convex portion provided on the opposing surface and having a radial dimension that is narrower than a radial dimension of the rotating ring; and the stationary ring is provided on the opposing surface of the rotating ring and is in the radial direction. A second convex portion whose dimension is narrower than a radial dimension of the stationary ring; and the axial end surface of the second convex portion slides with the axial end surface of the first convex portion. It is characterized by that.

  Further, the stationary ring is an end portion on the rotating ring side with respect to the axial direction of the shaft member, and has a chamfered portion on an outer peripheral edge portion thereof, and the second convex portion is radially inward of the chamfered portion. Is formed.

  Preferably, the chamfered portion is a stepped portion, or the chamfered portion is a tapered portion.

  Furthermore, both the axial end surface of the first convex portion and the axial end surface of the second convex portion are provided perpendicular to the axial direction of the shaft member.

  The mechanical device is preferably attached to a shaft member of the pump device.

  According to the present invention, the stationary ring has the second convex portion provided on the surface facing the rotating ring and having a radial dimension narrower than a radial dimension of the stationary ring. And the axial direction end surface of the 2nd convex part in a stationary ring slides with the axial direction end surface of the 1st convex part in a rotation ring. That is, since the second convex portion is narrowed, the area of the axial end surface of the second convex portion is smaller than the conventional one, and the axial end surface of the first convex portion is the axial end surface of the second convex portion. The area of the non-sliding surface that does not slide with the first convex portion can be made as small as possible while sufficiently securing the area of the sliding surface. In addition, since the area of the end surface in the axial direction of the second convex portion is small, the area of the surface to be processed on which high-precision processing such as surface roughness and flatness is performed can be reduced. Therefore, energy saving can be realized while maintaining good sealing performance, and the manufacturing cost can be greatly reduced.

  Further, by providing a chamfered portion on the outer peripheral edge portion of the end surface on the rotating ring side with respect to the axial direction of the shaft member of the stationary ring, a second convex portion is formed radially inward of the chamfered portion. When providing the chamfered portion and the second convex portion, it is only necessary to change a part of the mold for forming the fixed ring, so that the second convex portion can be easily formed on the fixed ring. Moreover, since the radial dimension of the stationary ring is not changed, there is no need to change the gasket molding die. Therefore, the mechanical seal device can be manufactured by a simple operation, and an increase in manufacturing cost can be suppressed.

It is a perspective view showing roughly the composition of the mechanical seal device concerning the embodiment of the present invention. It is sectional drawing which shows the state in which the mechanical seal apparatus of FIG. 1 was attached to the shaft member, (a) is a general view, (b) is an enlarged view of a sliding surface. (A) And (b) is sectional drawing which shows the modification of the stationary ring in FIG. It is a figure which shows the state which has arrange | positioned two mechanical seal apparatuses in parallel with the shaft member. It is sectional drawing which shows the structure of the conventional mechanical seal apparatus.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a perspective view schematically showing a configuration of a mechanical seal device according to an embodiment of the present invention. FIG. 2A is an overall view showing a state in which the mechanical seal device of FIG. 1 is attached to a shaft member. It is sectional drawing. The mechanical seal device of FIG. 1 is used in various industrial equipment, particularly pump devices, and is mounted on a shaft for the purpose of sealing an internal fluid or the like (hereinafter referred to as an object to be sealed) between a housing and a shaft member. The The mechanical seal device of FIG. 1 shows an example thereof, and the configuration of the mechanical seal device according to the present invention is not limited to that of FIG.

  The mechanical seal device 1 rotates together with a maining ring 20 (fixed ring) provided on the housing 60 side and a shaft member 50 and is urged in the axial direction by a spring described later to slide on the end surface of the maining ring 20. And a seal ring 10 (rotary ring) having a sliding surface that moves. The seal ring 10 and the maining ring 20 are a pair of annular members arranged coaxially, and the seal ring 10 and the maining ring 20 cooperate to seal the object to be sealed between the two members.

  A substantially funnel-shaped case 11 that is fitted to the seal ring is attached to the outer peripheral edge of the seal ring 10. The case 11 contains a bellows 12 made of resin or elastomer. The bellows 12 extends radially outward from the end of the cylindrical portion 12A and the cylindrical portion, and contacts the seal ring 10. And a flange portion 12B in contact or pressure contact. The drive ring 13 is disposed on the outer peripheral portion of the cylindrical portion 12A, and the cylindrical portion 12A is brought into close contact with the shaft member 50 by the fitting force of the drive ring, whereby the inner peripheral surface 12a of the cylindrical portion 12A and the shaft The object to be sealed is sealed with the outer peripheral surface 50 a of the member 50. Further, the flange portion 12 </ b> B has a protrusion 12 </ b> B ′ on the surface of the machine outside A, and the projecting direction end surface 12 b is in pressure contact with the machine end B end surface 10 a of the seal ring 10.

  Further, a spring holder 14 having a substantially L-shaped cross section fitted to the rotating shaft 50 is disposed on the machine inner side B of the case 11, and the case is placed on the machine outer side A between the spring holder and the case 11. An urging spring 15 is disposed. The spring 15 is a coil spring, but may be a conical spring, or may be a multi-spring type in which a plurality of coil springs are arranged around the shaft member in place of the single spring type as in the present embodiment. May be adopted.

  The seal ring 10, the case 11, and the bellows 12 rotate together with the shaft member 50 in a state where they are connected by the urging force of the spring 15. Further, the bellows 12 is elastically deformed in the axial direction of the shaft member 50, so that the seal ring 10 is urged toward the outside A. As described above, the seal ring 10 slides on the maining ring 20 by the urging force of the spring 15 and the bellows 12, and the object to be sealed is blocked by the sliding surface between the seal ring 10 and the mainting ring 20. As a result, even when wear occurs on the sliding contact surface between the seal ring 10 and the maining ring 20, it is possible to exhibit good sealing performance between these members.

  As shown in FIG. 2B, the seal ring 10 is an annular member having a substantially convex cross section in which an annular protrusion is integrally formed on the end surface of the machine outside A. Specifically, the seal ring 10 is provided on the surface facing the maining ring 20 and has a convex portion 10A (first convex portion) whose radial dimension W1 is narrower than the radial dimension W2 of the seal ring. )have.

  This seal ring 10 is made of an inorganic material, an inorganic compound, or a sintered body (ceramics) thereof, and may be carbon, silicon carbide, or a composite material in which another lubricating material is added to silicon carbide depending on the application. For example, carbon is used when emphasizing lubricity, and silicon carbide is used when emphasizing strength.

  Maining ring 20 is fixed to housing 60 via gasket 61 (FIG. 1). Inner peripheral surface 60a of housing 60 abuts on outer peripheral surface 61b of gasket 61, and inner peripheral surface 61a of gasket 61 is the main. It is in contact with the outer peripheral surface 20 b of the ting ring 20. The inner peripheral surface 20a of the maining ring 20 is separated from the outer peripheral surface 50a of the shaft member 50 at a constant interval. The maining ring 20 and the housing 60 are provided so as to be rotatable relative to the shaft member 50. In this embodiment, the maining ring 20 and the housing 60 are fixed, and the shaft member 50 is configured to be rotatable. However, the shaft member 50 may be fixed and the maining ring 20 and the housing 60 may be configured to be rotatable.

Specifically, as shown in FIG. 2B, the maining ring 20 is provided on the surface facing the seal ring 10, and the radial dimension W3 is narrower than the radial dimension W4 of the maining ring. 20A (second convex portion) that has been converted into a convex shape. 20 A of this convex part can be formed by providing a chamfering part over the perimeter in the peripheral part of the maining ring 20, for example. In the present embodiment, the maining ring 20 has an end portion on the seal ring 10 side in the axial direction of the shaft member 50 and has a stepped portion 22 (chamfered portion) on the outer peripheral edge portion 21 thereof. A convex portion 20 </ b> A is formed inward of the attached portion 22 in the radial direction. The maining ring 20 is usually provided with C chamfering at each of the four corners from the viewpoint of preventing breakage, but the chamfered portion in the present invention is obtained by C chamfering. The effect is different. The mainting ring 20 is made of a hard material made of an inorganic material, an inorganic compound, or a sintered body thereof, and examples thereof include alumina ceramics (Al ₂ O ₃ ) and silicon carbide (SiC). By forming the maining ring 20 with a material having a low friction coefficient as described above, the frictional force generated between the seal ring 10 and the maining ring 20 is reduced, and energy loss can be suppressed.

  The convex portion 10A of the seal ring 10 and the convex portion 20A of the maining ring 20 are arranged to face each other, and both the axial end surface 10b of the convex portion 10A and the axial end surface 20c of the convex portion 20A are both shaft members 50. It is provided perpendicularly to the axial direction. A sliding surface is formed by the axial end surface 20c of the convex portion 20A and the axial end surface 10b of the convex portion 10A. Moreover, in the part in which the stepped part 22 is formed, the seal ring 10 and the maining ring 20 do not slide, and the non-sliding surface (FIG. ) Range X).

  Further, in consideration of the shaft runout and eccentricity of the seal ring 10, in this embodiment, the radial dimension W3 on the axial end surface 20c of the convex portion 20A is larger than the radial dimension W1 on the axial end surface 10b of the convex portion 10A. Largely (W3> W1), sliding surfaces are respectively formed on the radially inner side and the outer side of the convex portion 10A. Thereby, when the seal ring 10 rotates with the rotation of the shaft member 50, even if axial runout or eccentricity occurs with respect to the rotation shaft of the shaft member 50, the axial end surface 10 b of the convex portion 10 </ b> A. The whole slides with the axial end surface 20c of the convex portion 20A, and a constant and sufficient sliding surface can be secured between the convex portion 10A and the convex portion 20A.

  The chamfered portion provided in the maining ring is not limited to the shape shown in FIG. 2B, and various shapes can be selected. For example, as shown in FIG. 3A, the chamfered portion is formed on the outer peripheral edge portion 31 of the maining ring 30 and has a tapered portion 32 (having an inclined surface 32a inclined with respect to the axial end surface 30c of the convex portion 30A. It may be a chamfer). Further, as shown in FIG. 3B, a protruding portion 40A protruding in the axial direction is provided at an end portion of the maining ring 40 on the axial seal ring 10 side, and a step is formed on the outer peripheral edge portion 41 of the protruding portion 40A. The part 42 may be formed. Even with such a configuration of the maining ring, while ensuring a non-sliding surface at the end of the maining ring on the seal ring 10 side, between the convex portion 10A and the convex portion 20A or between the convex portion 10A and the convex portion 20A, A constant and sufficient sliding surface can be ensured between.

  As described above, according to the present embodiment, the maining ring 20 is provided on the surface facing the seal ring 10, and the radial dimension W3 is narrower than the radial dimension W4 of the mainting ring. It has a convex portion 20A. Then, the axial end surface 20 c of the convex portion 20 </ b> A in the maining ring 20 slides with the axial end surface 10 b of the convex portion 10 </ b> A in the seal ring 10. That is, since the convex portion 20A is narrowed, the area of the axial end surface 20c of the convex portion 20A is smaller than the conventional one, and the axial end surface 20c of the convex portion 20A has the axial end surface 10b of the convex portion 10A. The area of the non-sliding surface that does not slide with the convex portion 10A can be made as small as possible while sufficiently securing the area of the sliding surface. Further, since the area of the axial end face 20c in the convex portion 20A is smaller than the conventional area, it is possible to reduce the area of the surface to be processed on which high-precision processing such as surface roughness and flatness is performed. Thereby, energy saving is implement | achieved, maintaining favorable sealing performance, and also the manufacturing cost of the mechanical seal apparatus 1 can be reduced significantly.

  Further, by providing a stepped portion 22 on the outer peripheral edge portion 21 on the end surface of the maining ring 20 on the axial direction seal ring 10 side, a convex portion 20A is formed radially inward of the chamfered portion. . When providing the stepped portion 22 and the convex portion 20A, it is only necessary to change a part of the mold for forming the mainting ring 20, and thus the convex portion 20A is easily formed on the mainting ring 20. can do. In addition, since the radial dimension of the maining ring 20 is not changed, it is not necessary to change the mold for forming the gasket 61. Therefore, the mechanical seal device 1 can be manufactured with a simple operation, and an increase in manufacturing cost can be suppressed.

  In particular, by attaching the mechanical seal device 1 to the rotating shaft of the pump device, various liquids such as water, seawater, and solution to be sealed can be reliably sealed between the seal ring 10 and the maining ring 20. it can.

  Although the mechanical seal device according to the above embodiment has been described above, the present invention is not limited to the described embodiment, and various modifications and changes can be made based on the technical idea of the present invention.

  In addition, the mechanical seal device of the above embodiment is an inside type in which the leakage direction of the sealing target on the sliding surface is opposite to the centrifugal force direction, but not limited to this, the outside A and the inside B are reversed. The outside shape in which the leakage direction of the sealing target on the sliding surface is the same as the centrifugal force direction may be used.

  The mechanical seal device of the above embodiment is an unbalanced type in which the outer diameter of the shaft member 50 is constant, but is not limited to this, and is a balanced type using shaft members having different outer diameters. Also good.

  It is also possible to arrange two mechanical seal devices side by side on the shaft member 50. For example, as shown in FIG. 4, a double-type mechanical seal structure in which two mechanical seal devices 1A and 1B are arranged in opposite directions can be provided. In this case, the external fluid is supplied at a pressure higher than the pressure to be sealed between the two sliding surfaces L and R in the axial direction. According to this structure, when used under a low pressure or when the liquid to be sealed has a high viscosity, the object to be sealed can be reliably sealed. Further, a tandem mechanical seal structure in which the two mechanical seal devices 1A and 1B are arranged in the same direction may be provided.

  The mechanical seal device of the present invention is suitably used for a rotating shaft of various pump devices, and is extremely useful as a mechanical seal device applied particularly to submersible pumps and land-based general-purpose pumps.

DESCRIPTION OF SYMBOLS 1 Mechanical seal apparatus 1A, 1B Mechanical seal apparatus 10 Seal ring 10A Convex part 10a End surface 10b Axial direction end surface 11 Case 12 Bellows 12A Cylindrical part 12a Inner peripheral surface 12b Projection direction end surface 12B Flange part 12B 'Protrusion 13 Drive ring 14 Spring holder 15 Spring 20 Maining ring 20A Convex portion 20b Outer peripheral surface 20a Inner peripheral surface 20c Axial end surface 21 Outer peripheral edge portion 22 Stepped portion 30 Mainting ring 30c Axial end surface 31 Outer peripheral edge portion 32 Tapered portion 32a Inclined surface 40 Mainting ring 40A Protruding portion 41 Outer peripheral edge portion 42 Stepped portion 50 Shaft member 50a Outer peripheral surface 60 Housing 60a Inner peripheral surface 61 Gasket 61a Inner peripheral surface 61b Outer peripheral surface A Outer machine side B Inner machine side W1 Radial dimension W2 Radial dimension W3 Radial dimension W4 radial dimension Law

Claims (6)

A mechanical seal that seals between the housing and the shaft member;
A stationary ring provided on the housing side;
A rotating ring having a sliding surface that rotates together with the shaft member and is urged in the axial direction by the urging member to slide with respect to an end surface of the fixed ring;
The rotating ring has a first convex portion provided on a surface facing the fixed ring and having a radial dimension narrower than a radial dimension of the rotating ring,
The stationary ring has a second convex portion provided on a surface facing the rotating ring and having a radial dimension narrower than a radial dimension of the stationary ring,
The mechanical seal device, wherein the axial end surface of the second convex portion slides with the axial end surface of the first convex portion. The stationary ring is an end portion on the rotating ring side with respect to the axial direction of the shaft member and has a chamfered portion on an outer peripheral edge portion thereof
The mechanical seal device according to claim 1, wherein the second convex portion is formed radially inward of the chamfered portion.   The mechanical seal device according to claim 2, wherein the chamfered portion is a stepped portion.   The mechanical seal device according to claim 2, wherein the chamfered portion is a tapered portion.   The axial end surface of the first convex portion and the axial end surface of the second convex portion are both provided perpendicular to the axial direction of the shaft member. The mechanical seal device according to any one of claims.   The mechanical seal device according to claim 1, wherein the mechanical seal device is attached to a shaft member of the pump device.

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