JP2005214276A - Sealing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sealing device wherein a protruding part can sufficiently exercise a function of permeation reduction. <P>SOLUTION: In a refrigerant compressor, the sealing device is characterized by that an elastic sealing member 41 interposed between faying surfaces 50 and 51 of housings is provided with an O-ring part 41a with a circular cross section, and a protrusion part 41b annularly formed on an outer circumference positioned in a low pressure side of the O-ring part 41a, and the protrusion part 41b is held between a cylinder block 11 and a rear housing 14 via a filling member 52 in a fastened and joined state of the cylinder block 11 and the rear housing 14. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a sealing device used in a joint portion of a housing in a fluid machine, for example.

  For example, a refrigerant compressor of an air conditioner includes a housing formed by fastening and coupling a plurality of housing constituents. A seal device using an O-ring is used for sealing between the housing components. When an O-ring is used for the sealing device, for example, the fastening force between the housing components is small as compared with the case where a gasket is used, and the stress acting on each housing component and internal components in the housing component. Has the advantage of being small.

  However, when an O-ring is used in the sealing device, even if the O-ring seals between the housing components, that is, the gap between the housing components is completely closed, Due to the material of the O-ring and the like, there is a problem that the refrigerant gas easily permeates from the inside of the refrigerant compressor to the outside. In particular, when carbon dioxide is used as the refrigerant, the pressure inside the machine (atmosphere side) becomes large because the inside of the machine has a much higher pressure compared to, for example, a fluorocarbon refrigerant. The problem of the permeation of the refrigerant gas was serious. On the other hand, it is known that the permeation of refrigerant gas can be reduced as the cross-sectional area of the permeating O-ring is smaller than the permeating direction of the refrigerant gas and the length of the permeating O-ring is longer in the permeating direction. ing.

  Therefore, in order to solve the problem of refrigerant gas permeation through the O-ring, for example, it is conceivable to apply the elastic seal member disclosed in Patent Document 1 to a seal device of a refrigerant compressor. FIG. 6 is a longitudinal sectional view of the sealing device. As shown in FIG. 6, an elastic seal member 103 is interposed between the joint surface 101 a of the housing component 101 and the joint surface 102 a of the housing component 102. Yes. Here, in FIG. 6, the upper side of the drawing is the inside of the machine, and the lower side of the drawing is the outside of the machine. Further, the inside of the machine is the high pressure side, and the outside of the machine is the low pressure side.

  5 is an overall front view of the elastic seal member 103 as viewed from the direction 1-1 in FIG. The elastic seal member 103 has an O-ring part 103a having a circular cross section, and a protrusion formed annularly along the outer periphery of the O-ring part 103a with the center O of the O-ring part 103a as the center of the circle as shown in FIG. Part 103b. A length D2 (hereinafter simply referred to as a thickness) D2 in the direction perpendicular to the radial direction centering on the center O of the O-ring portion 103a of the protrusion 103b is smaller than the thickness D1 of the O-ring portion 103a. In order to suppress the permeation of the refrigerant gas, unlike Patent Document 1, the protrusion 103b of the elastic seal member 103 is disposed along the joint surfaces 101a and 102a and is sandwiched between the joint surfaces 101a and 102a. There is a need.

Therefore, in addition to the length H1 in the direction along the joint surfaces 101a and 102a of the O-ring portion 103a, that is, the radial direction centered on the center O of the O-ring portion (hereinafter referred to as the radial direction), the radial direction in the protruding portion 103b. The extension length of the elastic seal member 103 can be increased by the length H2 as compared with the sealing device in the case of only the O-ring portion 103a having no protrusion 103b. Further, by making the thickness D2 of the protrusion 103b smaller than the thickness D1 of the O-ring portion 103a, the cross-sectional area through which the refrigerant gas permeates the elastic seal member 103, that is, the area of the surface perpendicular to the radial direction is the protrusion 103b. Therefore, the area is smaller than that in the O-ring portion 103a. Accordingly, the length of transmission in the transmission direction in the elastic seal member 103 can be increased and the cross-sectional area of transmission can be reduced, so that it is difficult for the refrigerant gas to pass through the elastic seal member 103.
Japanese Patent Laid-Open No. 11-2327 (page 3, FIG. 1)

  However, the gap of the gap between the joining surface 101a and the joining surface 102a of the refrigerant compressor varies from one unit to another due to, for example, tolerance of parts in the machine. As a result, when the elastic seal member 103 is used, the gap between the joint surface 101a and the joint surface 102a, which is planned in design, becomes wider, and after the fastening connection between the housing components 101 and 102, A gap may be generated between the protrusion 103b and the housing component 101 or between the protrusion 103b and the housing component 102. If the gap is generated, the refrigerant gas passes through the O-ring portion 103a of the elastic seal member 103 and then does not attempt to pass through the protrusion 103b, but between the protrusion 103b and the housing component 101. Or a gap between the protrusion 103b and the housing component 102. Therefore, the protrusion 103b may not be able to fully exhibit the function of reducing transmission as described in the background art.

  Further, in order to prevent a gap from being formed between the projection 103b and the housing components 101, 102, the thickness D2 ′ of the projection 103b before the housing components 101, 102 are joined together is determined by the components in the machine. There is a way to make it thick enough for possible tolerances. However, when this method is used, when the tolerance of the parts in the machine is small, the thickness of the protrusion 103b is larger than the gap between the joint surfaces 101a and 102a generated when the housing components 101 and 102 are fastened and joined. Since the case where D2 ′ is too thick may occur, when trying to set the gap interval, the protrusion 103b must be crushed until the gap is reached. Therefore, depending on the tolerance, the width (hereinafter simply referred to as crushing allowance) in which the protrusion 103b is compressed in the direction perpendicular to the radial direction becomes excessive, and the fastening force between the housing components 101 and 102 must be increased. Will happen. Therefore, the advantage of using the O-ring, that is, the advantage that the fastening force between the housing structural members 101 and 102 is small is lost.

  An object of the present invention is to provide a sealing device using an elastic seal member having an O-ring portion and a protruding portion, in which the protruding portion can sufficiently exhibit a function of reducing permeation.

  In order to achieve the above object, in the sealing device according to claim 1, the protrusion is sandwiched between the joining surfaces of the first member and the second member via the filling member. .

  Therefore, for example, when the gas on the high pressure side attempts to permeate the O-ring part in the elastic seal member, the gap between the protrusion part and the first member and the protrusion part and the first part in the protrusion part located on the low pressure side from the O-ring part. The gas that has permeated through the O-ring part through the gap between the two members can be prevented from escaping, and the gas that has permeated through the O-ring part is guided so as to permeate through the protrusion. That is, the permeation distance that must pass through when the gas permeates the O-ring portion can be increased. Therefore, the protrusion can sufficiently perform the function of reducing transmission.

  According to a second aspect of the present invention, in the first aspect, the low pressure side tip surface of the filling member is positioned at least on the low pressure side than the low pressure side tip surface of the protrusion.

  Therefore, for example, when the low pressure side tip surface of the filling member is not located on the low pressure side from the low pressure side tip surface of the protrusion, the gas that has permeated through the protrusion will escape from the low pressure side tip surface of the protrusion. Instead, it escapes from the gap between the low pressure side protrusion and the joint surface from the low pressure side tip surface of the filling member. However, in the present invention, since the low pressure side tip surface of the filling member is located on the low pressure side from the low pressure side tip surface of the projection, the gas permeates when passing through the low pressure side tip surface of the projection. Since the transmission distance can be set, it is possible to improve the function of reducing transmission by forming the protrusions.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, the high pressure side tip surface of the filling member is in contact with the O-ring portion.

  Therefore, there is no gap between the O-ring part and the filling member, and the O-ring part, the protrusion, and the joining surface of the first member or the joining surface of the second member are surely lower than the O-ring part. A gap surrounded by three can be eliminated. Therefore, it is possible to suppress the gas that attempts to permeate the O-ring part from leaking into the gap formed between the O-ring part and the filling member.

  The invention according to claim 4 is the invention according to any one of claims 1 to 3, wherein the filling member is at least a thickness of the first member in a state where the first member and the second member are joined. It is thicker than the difference between the distance between the first member and the second member and the thickness of the protrusion in the state before joining the first member and the second member.

Therefore, the protrusion is crushed by providing the filling member. That is, when the protrusion is crushed, the surface pressure between the protrusion and the filling member increases, and between the filling member and the first member and / or between the filling member and the second member, the protrusion The surface pressure between the first member and / or between the protrusion and the second member will increase. Therefore, at the position of the protrusion, the sealing effect between the protrusion and the first member and between the protrusion and the second member is also increased, and even though the gas has permeated the O-ring part, the O-ring part has permeated. Since the gas can be guided more reliably so as to permeate the inside of the protrusion, the function of reducing transmission due to the formation of the protrusion can be further enhanced.

According to the seal device of the first to fourth aspects of the present invention, in the elastic seal member having the O-ring portion and the protrusion, the refrigerant gas permeates through the gap between the first member, the second member, and the protrusion by the filling member. Thus, the protrusion is suppressed, and the protrusion can sufficiently perform the function of reducing transmission.

  Hereinafter, a first embodiment and a second embodiment in which the sealing device of the present invention is applied to a refrigerant compressor constituting a refrigeration circuit of a vehicle air conditioner will be described. In the second embodiment, only differences from the first embodiment will be described, and the same or corresponding members will be denoted by the same reference numerals and description thereof will be omitted.

First Embodiment First, a refrigerant compressor as a fluid machine will be described.

  FIG. 1 shows a longitudinal sectional view of a refrigerant compressor. In FIG. 1, the left side is the front of the refrigerant compressor, and the right side is the rear of the refrigerant compressor. As shown in FIG. 1, the housing of the refrigerant compressor includes a cylinder block 11, a front housing 12 joined to the front end of the cylinder block 11, and a rear housing 14 joined to the rear end of the cylinder block 11. ing. That is, the cylinder block 11, the front housing 12, and the rear housing 14 form a housing structure that constitutes the housing of the refrigerant compressor. The cylinder block 11, the front housing 12, and the rear housing 14 are fastened and coupled to each other by a plurality of through bolts 15 (only one is shown). A valve / port forming body 13 is interposed between the cylinder block 11 and the rear housing 14.

  A crank chamber 16 is defined between the cylinder block 11 and the front housing 12 in the housing. A drive shaft 17 is rotatably supported between the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 16. The drive shaft 17 is rotationally driven by a vehicle engine (not shown). A rotor 18 is fixed to the drive shaft 17 in the crank chamber 16 so as to be integrally rotatable. A swash plate 19 is accommodated in the crank chamber 16. The swash plate 19 is supported by the drive shaft 17 so as to be slidable and tiltable.

  A hinge mechanism 20 is interposed between the rotor 18 and the swash plate 19. The swash plate 19 can be rotated synchronously with the rotor 18 and the drive shaft 17 by the hinge connection with the rotor 18 via the hinge mechanism 20 and the support of the drive shaft 17, and in the axial direction of the drive shaft 17. It is possible to tilt with respect to the drive shaft 17 with the sliding movement.

  In the cylinder block 11, cylinder bores 22 are formed around the axis L of the drive shaft 17 in the front-rear direction (left-right direction on the paper surface) at equal angular intervals. The single-headed piston 23 is accommodated in each cylinder bore 22 so as to be movable in the front-rear direction. The front / rear opening of the cylinder bore 22 is closed by the front end of the valve / port forming body 13 and the piston 23, and a compression chamber 24 whose volume changes in accordance with the movement of the piston 23 in the front / rear direction is defined in the cylinder bore 22. Has been. Each piston 23 is anchored to the outer periphery of the swash plate 19 via a pair of shoes 25. Accordingly, when the swash plate 19 is rotated by the rotation of the drive shaft 17, the swash plate 19 is swung back and forth in the direction of the axis L of the drive shaft 17. As the swash plate 19 swings, the piston 23 is reciprocated linearly in the front-rear direction.

  A suction chamber 26 and a discharge chamber 27 are defined between the valve / port forming body 13 and the rear housing 14 in the housing. The valve / port forming body 13 is formed with a suction port 28 and a suction valve 29 so as to be positioned between the compression chamber 24 and the suction chamber 26. A discharge port 30 and a discharge valve 31 are formed in the valve / port forming body 13 so as to be positioned between the compression chamber 24 and the discharge chamber 27.

  The refrigerant gas in the suction chamber 26 is sucked into the compression chamber 24 through the suction port 28 and the suction valve 29 by the movement from the top dead center position to the bottom dead center position of each piston 23. The refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by the movement from the bottom dead center position of the piston 23 to the top dead center position side, and enters the discharge chamber 27 via the discharge port 30 and the discharge valve 31. Discharged. Carbon dioxide is used as a refrigerant for the vehicle air conditioner.

  An extraction passage 32, an air supply passage 33, and a control valve 34 are provided in the housing of the compressor. The extraction passage 32 connects the crank chamber 16 and the suction chamber 26. The air supply passage 33 connects the discharge chamber 27 and the crank chamber 16. A control valve 34 is disposed in the supply passage 33. By adjusting the opening degree of the control valve 34, the balance between the amount of high-pressure discharge gas introduced into the crank chamber 16 through the air supply passage 33 and the amount of gas discharged from the crank chamber 16 through the extraction passage 32. And the internal pressure of the crank chamber 16 is determined. In accordance with the change in the internal pressure of the crank chamber 16, the difference between the internal pressure of the crank chamber 16 and the internal pressure of the compression chamber 24 via the piston 23 is changed, and the inclination angle of the swash plate 19 is changed. That is, the discharge capacity of the refrigerant compressor is adjusted.

  Next, sealing devices 39 and 40 applied to the refrigerant compressor, more specifically, a sealing device 39 used for a joint portion between the front housing 12 as the first member and the cylinder block 11 as the second member, and the first A sealing device 40 used in a joint portion between the rear housing 14 as a member and the cylinder block 11 as a second member will be described with reference to FIG. 2 which is an enlarged cross-sectional view of a circle A in FIG. In FIG. 2, the upper side of the drawing is the machine inside, the lower side of the drawing is the machine outside, the machine inside is the high pressure side, and the machine outside is the low pressure side. In FIG. 1, the radial direction of the drive shaft 17 corresponds to the vertical direction in FIG. 2 (hereinafter simply referred to as the radial direction). Further, the seal device 39 used at the joint portion between the front housing 12 and the cylinder block 11 has the same configuration as the seal device 40 used at the joint portion between the cylinder block 11 and the rear housing 14, and is shown in FIG. Corresponding members are numbered in parenthesis and detailed description is omitted.

  As shown in FIG. 2, an elastic seal member 41 is interposed between the joint surface 51 at the rear end of the cylinder block 11 and the joint surface 50 at the front end of the rear housing 14. The elastic seal member 41 is made of rubber such as hydrogenated acrylonitrile / butadiene rubber, for example. The structure of the elastic seal member 41 is the same as that of the elastic seal member 103 described in the prior art. The equivalent members shown in FIG. 5 are indicated by numbers in parentheses, and the elastic seal member 41 is used with reference to FIGS. The structure of will be described.

  The elastic seal member 41 is formed in an annular shape along the outer periphery on the outer peripheral side of the O-ring portion 41a, with the O-ring portion 41a having a circular cross section and the center O of the O-ring portion 41a as the center of the circle as shown in FIG. And a protrusion 41b. That is, when the rear housing 14 and the cylinder block 11 are fastened and joined, the O-ring portion 41a and the cylinder block 11 are formed so as to be along the joint surface 51 from the contact position 45 between the O-ring portion 41a and the outer side on the low pressure side of the O-ring portion 41a. It consists of a protrusion 41b. In a state before the elastic seal member 41 is fastened to the housing, the length of the cross section in the direction perpendicular to the radial direction of the protrusion 41b (hereinafter simply referred to as thickness) is thinner than the thickness of the O-ring portion 41a. . That is, the area of the surface perpendicular to the radial direction of the protrusion 41b is smaller than the area of the surface perpendicular to the radial direction of the O-ring portion 41a.

  An annular body housing groove 44 is formed on the joint surface 50 of the rear housing 14. The O-ring portion 41a of the elastic seal member 41 is housed and held in the main body housing groove 44 when the rear housing 14 and the cylinder block 11 are fastened and coupled. Between the protrusion 41b and the rear housing 14, a planar annular filling member 52 is provided along the protrusion 41b and the rear housing 14 in a gap generated when the rear housing 14 and the cylinder block 11 are fastened and coupled. Yes. The filling member 52 is made of a metal such as copper, for example. The length h3 in the radial direction of the filling member 52 is the front end surface on the outboard side as the low pressure side front end surface of the projecting portion 41b from the root of the O ring portion 41a of the projecting portion 41b when the rear housing 14 and the cylinder block 11 are fastened and joined. A length h2 or more up to 43 is secured. That is, the outboard front end surface 52b as the low pressure side front end surface of the filling member 52 is located on the low pressure side (outside of the machine side) than the outboard front end surface 43 as the low pressure side front end surface of the protrusion 41b. The in-machine front end surface 52a as the high-pressure side front end surface of the filling member 52 is in contact with the out-of-machine front end surface 42 of the O-ring portion 41a.

  Further, the thickness d3 of the filling member 52 is set between the protrusion 41b and the rear housing 14 when the rear housing 14 and the cylinder block 11 are fastened after measuring the dimensions of the parts inside the machine. Calculate the possible gap spacing d4. Next, a width (hereinafter simply referred to as a crushing margin) in which the protrusion 41b is compressed in a direction perpendicular to the radial direction in accordance with the distance d4, that is, the protrusion 41b before the fastening connection between the rear housing 14 and the cylinder block 11 is performed. The difference between the thickness d2 ′ of the protrusion 41b and the thickness d2 of the projection 41b in the state crushed by the fastening connection between the rear housing 14 and the cylinder block 11 is always fastened when the rear housing 14 and the cylinder block 11 are fastened and connected. The thickness d3 of the filling member 52 is set so that the force does not become too large. Specifically, several types of filling members 52 having different thicknesses are prepared, and one filling member corresponding to the calculation is selected and used.

  In the present embodiment having the above-described configuration, the following effects are obtained.

  (1) A filling member 52 is provided in the gap between the protrusion 41b and the rear housing 14. Therefore, when the refrigerant gas inside the machine attempts to permeate through the O-ring portion 41a in the elastic seal member 41, the refrigerant gas that has permeated through the O-ring portion 41a does not pass through the projecting portion 41b as it is, and the projecting portion 41b and the rear It is possible to suppress leakage through the gap with the housing 14 and leakage outside the machine. The refrigerant gas that has passed through the O-ring portion 41a is guided by the filling member 52 so as to pass through the projection 41b. That is, the permeation distance that the refrigerant gas must pass when passing through the elastic seal member 41 can be made longer than the radial length h1 of the O-ring portion 41a. Therefore, the protrusion 41b can sufficiently fulfill the function of reducing transmission.

  (2) The outboard tip surface 52b as the low pressure side tip surface of the filling member 52 is located on the low pressure side (outside of the device) than the outboard tip surface 43 as the low pressure side tip surface of the protrusion 41b.

  Therefore, when the machine-side front end surface 52b of the filling member 52 is not located outside the machine side from the machine-side front end surface 43 of the protrusion 41b, the refrigerant gas that has permeated through the protrusion 41b is outside the machine of the protrusion 41b. Instead of trying to escape from the front end surface 43, the filling member 52 escapes from the outboard front end surface 52 b into the gap between the outboard side projection 41 b and the rear housing 14.

  However, in this embodiment, the outboard front end surface 52b of the filling member 52 is located on the outboard side of the outboard end surface 43 of the protrusion 41b, so that the refrigerant gas reaches the outboard end surface 43 of the protrusion 41b. The transmission distance can be a transmission distance when transmitting. That is, in addition to the radial length h1 in the O-ring portion 41a, the radial length h2 in the projection 41b can also be a transmission distance, so that the function of reducing transmission by forming the projection 41b is improved. Can do.

  (3) The machine inner front end face 52a of the filling member 52 is in contact with the machine outer front end face 42 of the O-ring portion 41a. If there is a gap between the outboard tip surface 42 of the O-ring portion 41a and the inboard tip surface 52a of the filling member 52, the O-ring portion 41a is transmitted through the O-ring portion 41a at the shortest distance. The refrigerant gas escapes into the gap between the surface 42 and the inboard end surface 52a of the filling member 52.

  However, in the present embodiment, there is no gap between the in-machine front end surface 52a of the filling member 52 and the out-of-machine front end surface 42 of the O-ring portion 41a, so that the refrigerant gas that has passed through the O-ring portion 41a is filled with the filling member 52. It is also possible to suppress slipping out into the gap between the machine inner front end face 52a and the machine outer front end face 42 of the O-ring portion 41a.

  (4) By adjusting the thickness d3 of the filling member 52, the projection 41b can be crushed with a desired crushing margin, so that the gap between the projection 41b and the cylinder block 11 and the projection 41b and the filling member 52 The sealing performance can be improved between the filling member 52 and the rear housing 14.

  Therefore, since the refrigerant gas that has passed through the O-ring portion 41a can be guided more reliably so as to pass through the projection 41b, the function of reducing transmission due to the formation of the projection 41b is provided to the projection 41b. This can be higher than when no crushing cost is generated. Further, since the crushing margin does not become excessive as compared with the desired crushing margin, an increase in the fastening force when the rear housing 14 and the cylinder block 11 are fastened can be suppressed.

  (5) The filling member 52 is formed of a metal such as copper. Since metal is superior in gas permeability resistance compared to rubber or the like, the refrigerant gas does not permeate through the filling member 52. Further, in order to keep the crushing margin of the projection 41b constant, the filling member 52 made of metal does not need to consider elastic deformation, so it is easy to adjust the crushing margin of the projection 41b.

Second Embodiment FIG. 3 shows a second embodiment. In the present embodiment, an L-shaped portion 53 is provided on the machine-side front end surface 52 a of the filling member 52 of the first embodiment, and the L-shaped portion 53 is formed between the machine-side side surface 54 of the main body accommodation groove 44 and the joining surface 50. A filling member 52 is provided so as to be caught by the corner portion 55.

  Also in this embodiment, since the filling member 52 is provided between the protrusion 41b and the joint surface 50 as in the first embodiment, the protrusion 41b can sufficiently perform the function of reducing transmission.

  Furthermore, the filling member 52 can be positioned on the joint surface 50 by the L-shaped portion 53. Further, since the filling member 52 comes into contact with the machine outer side surface 54 of the main body accommodation groove 44 by the L-shaped portion 53, when the O-ring portion 41 a of the elastic seal member 41 is crushed by the internal pressure, the O-ring portion 41 a becomes the filling member 52. A force acts so as to press against the machine side surface 54 of the main body accommodation groove 44.

  Accordingly, when the internal pressure is increased, the sealing performance between the main body accommodation groove 44 and the L-shaped portion 53 of the filling member 52 is improved, so that the sealing performance between the filling member 52 and the rear housing 14 is improved. Therefore, it is possible to suppress the refrigerant gas from slightly leaking between the filling member 52 and the rear housing 14 after the refrigerant gas has permeated through the O-ring portion 41a.

For example, the following embodiments can also be implemented without departing from the spirit of the present invention.
○ The first embodiment is changed, and the filling member 52 is provided between the protruding portion 41 b and the cylinder block 11. Alternatively, the filling member 52 is provided both between the protrusion 41 b and the cylinder block 11 and between the protrusion 41 b and the rear housing 14.

  In each of the above embodiments, the protrusion 41b is set to obtain a crushing margin when the housing is fastened. However, the filling member 52 is sandwiched between the protrusion 41b and the joint surface 50 when the housing is fastened. However, the crushing margin of the protrusion 41b may be set to zero.

  In each of the above embodiments, when the housing is fastened, the filling member 52 is filled so that the gap between the protrusion 41b and the rear housing 14 is completely filled from the root of the protrusion 41b to the front end surface 43 of the protrusion 41b. The filling member 52 may be provided so as to eliminate a part of the gap between the protrusion 41b and the rear housing 14 as shown in FIG. The length h3 in the radial direction of the filling member 52 is shorter than the length h2 in the radial direction of the projection 41b, and the filling member 52 is located within the range of the length h2 of the projection 41b. Even if it does in this way, compared with the case where the filling member 52 is not in the clearance gap between the projection part 41b and the rear housing 14, the refrigerant gas which permeate | transmitted the inside of the O-ring part 41a by guidance of the filling member 52 is guided to the projection part 41b. Therefore, the protrusion 41b can exhibit the function of reducing transmission.

  In each of the above embodiments, the present invention is applied to the elastic seal member in which the protruding portion 41b is formed so as to extend from the contact position 45 between the O-ring portion 41a and the cylinder block 11 along the machine outer side which is the low-pressure side of the O-ring portion 41a. Had been applied. By changing this, the projection 41b may be applied to an elastic seal member formed by protruding from any position on the outer side surface of the O-ring portion 41a. For example, the present invention may be applied to an elastic seal member in which the protrusion 41b is formed so as to extend from the outermost peripheral position in the radial direction of the O-ring portion 41a to the outside of the machine on the low pressure side.

  In the above embodiments, the cross-sectional shape of the O-ring portion 41a is circular, but the cross-sectional shape of the O-ring portion 41a is not limited to a circular shape, and may be, for example, a quadrangle or a triangle.

  In each of the above embodiments, the filling member 52 is made of a metal such as copper, but may be made of an elastic member such as rubber.

  In the first embodiment, several types of filling members 52 having different thicknesses are prepared, and one of them is selected and used to fill the gap between the protrusion 41b and the rear housing 14. It was. By changing this and using a plurality of filling members 52 in a stacked manner, the gap between the protrusion 41b and the rear housing 14 may be filled.

  In each of the above embodiments, the sealing devices 39 and 40 using the present invention are applied to the joint portion between the front housing 12 and the cylinder block 11 and the joint portion between the cylinder block 11 and the rear housing 14, respectively. It was. However, the present invention is not limited to this, and the sealing device of the present invention is applied to one of the joint portion between the front housing 12 and the cylinder block 11 and the joint portion between the cylinder block 11 and the rear housing 14. For example, a sealing device using a gasket may be applied.

In each of the above embodiments, the outer peripheral side of the O-ring portion 41a is the low pressure side. However, for example, when the sealing device of the present invention is used for sealing a vacuum vessel or the like, the inner peripheral side of the O-ring portion 41a is the low pressure side. In some cases, permeation occurs from outside the machine. In this case, a protrusion is formed at least on the inner periphery of the O-ring portion 41a, and the filling member 52 is accordingly disposed on the inner periphery side of the O-ring portion 41a.
The technical idea that can be grasped from each of the above embodiments or other examples will be described below.

  (1) The sealing device according to any one of claims 1 to 4, wherein the filling member is made of metal.

  (2) A fluid machine including the sealing device according to any one of claims 1 to 4 or the technical idea (1).

The longitudinal cross-sectional view of the refrigerant compressor according to 1st Embodiment of this invention. The enlarged view in the circle A of FIG. The cross-sectional enlarged view of the sealing device according to 2nd Embodiment of this invention. The cross-sectional enlarged view of the sealing apparatus used as another example. The front whole figure of the elastic sealing member used for the conventional sealing apparatus. The cross-sectional enlarged view of the conventional sealing apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 ... Cylinder block as 1st member, 12 ... Front housing as 2nd member, 14 ... Rear housing as 2nd member, 39, 40 ... Sealing device, 41 ... Elastic sealing member, 41a ... O-ring part, 41b ... Projection, 50... The front housing and the cylinder block are joined by the front housing. The cylinder block and the rear housing are joined by the rear housing. 51. The cylinder block is joined by the 52. ..Filling members

Claims (4)

An O-ring part between the joint surface of the first member and the joint surface of the second member, and at least the pressure on the inner peripheral side and the pressure on the outer peripheral side of the O-ring part among the outer periphery and inner periphery of the O-ring part In a sealing device provided with an elastic seal member comprising a protrusion portion having a thickness smaller than the thickness of the O-ring portion formed annularly on one side positioned on the low pressure side,
The sealing device, wherein the protrusion is sandwiched between a joining surface of the first member and the second member via a filling member.   2. The sealing device according to claim 1, wherein the low pressure side tip surface of the filling member is positioned at least on the low pressure side than the low pressure side tip surface of the protrusion.   3. The sealing device according to claim 1, wherein a high-pressure-side front end surface of the filling member is in contact with an O-ring portion.   The filling member has at least a thickness, a distance between the first member and the second member in a state in which the first member and the second member are fastened, and a state before the first member and the second member are fastened. The sealing device according to any one of claims 1 to 3, wherein the sealing device is thicker than a difference between the thickness of the protruding portion.

Images