WO2006112050A1

WO2006112050A1 - Structure for preventing leakage of refrigerant from portion at which compressor-constituting part is fastened

Info

Publication number: WO2006112050A1
Application number: PCT/JP2005/016425
Authority: WO
Inventors: Hironobu Deguchi; Sakae Hayashi; Shunichi Furuya; Hiroshi Kanai
Original assignee: Valeo Thermal Systems Japan Corporation
Priority date: 2005-03-31
Filing date: 2005-09-07
Publication date: 2006-10-26
Also published as: JP2006283560A

Abstract

A seal mechanism for preventing leakage of a refrigerant from a compressor. In the seal mechanism, seal members are singly placed at fastening portions between a housing of the compressor and compressor constituting parts such as a piping connector and a pressure control valve. Further, in the seal mechanism, the amount of a CO2 refrigerant permeating through the cylindrical seal members is reduced and at the same time the seal mechanism is prevented from becoming complex as a seal mechanism and large in size. In fastening compressor constituting parts (35, 38) having cylindrical surfaces to a housing (2), a cylindrical surface seal member (55) is placed at fastening portions between the compressor constituting parts (35, 38) having cylindrical surfaces and the housing (2), the cylindrical surface seal member (55) being a tubular body open at both sides in the axial direction and is greater in dimension than the wall thickness of a side section of the tubular body, the cylindrical surface seal member (55) being interposed in an orientation providing a pressure difference such that one side in the axial direction of the seal member (55) is on the high-pressure side and the other is on the low-pressure side.

Description

Specification

Refrigerant leakage prevention structure from fastening parts of compressor components

Technical field

[0001] In the present invention, when a substantially columnar component such as a pressure control valve of a compressor is assembled and fastened to a housing of the compressor, the refrigerant passes from the fastening portion into the outside of the compressor or adjacent to the inside of the compressor. The present invention relates to a structure for preventing leakage into a space.

Background art

[0002] When a component having a cylindrical surface of a compressor is fastened to a compressor housing in a highly airtight manner, for example, as shown in Patent Document 1, a capacity control valve is provided on the peripheral surface of the rear block of the compressor. When inserting and assembling into the opened hole, an O-ring is attached in advance to the side of the capacity control valve to seal the gap between the peripheral surface of the side of the capacity control valve and the inner peripheral surface of the hole. As such a cylindrical surface sealing member, it has been common to use a single and general o-ring made of rubber.

[0003] However, in recent years, as shown in Patent Documents 2, 3, and 4, for example, air conditioners that use carbon dioxide (CO) as a refrigerant have been developed.

2

In existing single-material rubber O-rings, CO refrigerant passes through the O-ring and pressurizes.

2

The amount of refrigerant leaking into the atmosphere outside the compressor is increased, and there is a problem in that the sealing performance between the component having the cylindrical surface of the compressor and the compressor housing cannot be secured. Has reached.

[0004] For the problem of CO refrigerant permeating through such an O-ring, for example, the above-mentioned patent document

2

As shown in FIG. 2, an invention has been made to solve the problem by improving the O-ring itself by adopting butyl rubber, particularly halogenated butyl rubber, as the rubber material of the O-ring. For example, as shown in Patent Documents 3 and 4, the rubber material for the seal member is made of CO-cooled.

2 An invention has also been made in which an NBR-based polymer containing bound acrylonitrile having a property that the medium is difficult to permeate is combined, and the content of the bound acrylonitrile is 45% by weight or more.

[0005] Furthermore, as shown in FIG. 3 of Patent Document 5, for example, the same tightening of the components of the compressor is performed. The o-ring is doubled for the ligation site, and the inner o-ring uses a material with excellent mechanical and chemical properties (nitrile rubber), and the outer o-ring is resistant to gas. An invention has been made in which an excellent material (putil rubber) is used, the inner o-ring has a large diameter, and the outer o-ring has a small diameter. For example, as shown in Patent Document 6, a seal mechanism interposed on a joint surface between members constituting each housing of the compressor includes a plurality of seal members, and these seal members are arranged inside the housing. There is also an invention in which the gasket and the outside of the housing are arranged so as to be O-rings.

Patent Document 1: Japanese Patent Application Laid-Open No. 2003-328936

Patent Document 2: JP 2002-12852

Patent Document 3: Japanese Patent Laid-Open No. 2003-246976

Patent Document 4: EP 1 321 499A2 Publication

Patent Document 5: JP 2000-170656 A

Patent Document 6: Japanese Patent Application Laid-Open No. 2002-317764

Disclosure of the invention

Problems to be solved by the invention

[0006] However, when the butyl rubber shown in Patent Document 2 is used as the material for the O-ring, the density of butyl rubber is relatively high, so that it is not elastic in a cold environment where the temperature is extremely low. , Tend to be inferior in cold resistance. For this reason, in winter in cold regions, for example, external shocks cannot be sufficiently absorbed by the O-ring, creating a gap. Even if the CO 2 refrigerant does not pass through the O-ring, the compressor passes through this gap. There is a concern that it will leak to the outside. In addition, regarding the inventions shown in Patent Documents 3 and 4, acrylonitrile rubber is said to be useful as a high-performance rubber with high strength, heat resistance, and cold resistance improved by hydrogenation treatment and the like. Force There is a problem that the greater the nitrile content, the worse the compression set, and the gap force generated on the outer peripheral surface or inner peripheral surface of the seal member.

[0007] Then, in order to seal the same fastening portion between the compressor component and the compressor housing, a seal mechanism configured with a plurality of O-ring forces as shown in Patent Document 5, or a patent document When using a seal mechanism consisting of an O-ring and gasket as shown in Fig. 6. In this case, the seal mechanism and its peripheral part are relatively complicated and large, and the compressor that accommodates the seal mechanism is also large, so that it is not possible to meet the recent demand for space saving of the compressor mounting capacity. Inconveniences and an increase in the number of parts, which in turn increases the overall manufacturing cost of the compressor.

[0008] In view of the above, the present invention aims to prevent refrigerant leakage with respect to a compressor using CO refrigerant as the refrigerant.

2

As a sealing mechanism, the amount of CO refrigerant that permeates the cylindrical surface sealing member is reduced while the sealing member is disposed alone at the fastening portion with the compressor housing, and the sealing mechanism

2

The purpose is to both increase the complexity, increase the size of the compressor, increase the size of the compressor, and prevent the manufacturing cost of the entire compressor from increasing.

Means for solving the problem

[0009] The refrigerant leakage prevention structure from the fastening part of the compressor component according to the present invention includes a housing, a drive shaft that is rotatably supported by the housing and rotated by an external driving force, and the drive In a compressor having a drive mechanism for converting the rotational movement of the shaft into a compressing action of the refrigerant, when fastening a compressor component having a cylindrical surface such as the piping connector or a pressure control valve to the housing, Between the housing and the compressor connector having a cylindrical surface such as the piping connector or the pressure control valve, a cylindrical body is opened on both sides in the axial direction, and the dimension along the axial direction is the thickness of the side surface. A cylindrical seal member for a compressor having a size larger than that of the compressor is interposed such that one of the axial directions thereof is on the high pressure side and the other is in the direction of the pressure difference from the low pressure side (claim 1). This type of compressor is not only a piston type, rotary type, scroll type, but also a type of compressor that does not have a shaft seal between the drive shaft and the housing, such as an electric compressor. Applied. In addition, this cylindrical surface sealing member has a compression ratio of, for example, 20% in order to ensure a sealing function when inserted, and at the same time to prevent high compression set and high compression set and shorten its life. 70%.

[0010] The cylindrical surface sealing member for a compressor may have an extending portion extending radially outward from the opening (claim 2). On the contrary, the cylindrical surface sealing member for the compressor may have an extension portion extending radially inward of the opening force (claim 3). The cylindrical surface sealing member for the compressor is formed on the outer peripheral surface of the cylindrical body. A plurality of convex portions may be provided so as to form a da-shape (claim 4).

The cylindrical surface sealing member for a compressor may be made of an elastomer material force mainly composed of hydrogenated-tolyl rubber (claim 5). In this case, the elastomer material forming the cylindrical surface sealing member for the compressor is characterized in that the hydrogenated-tolyl rubber has a tolyl content not exceeding 45% (Claim 6). . On the other hand, the cylindrical surface sealing member for the compressor may be made of an elastomer material sheet mainly composed of silicon rubber (claim 7).

[0012] Further, it is optimal that the cylindrical surface sealing member for a compressor has a dimension along the axial direction of 2 mm to 2 Omm, and a side wall thickness of 0.5 mm to 3 mm. (Claim 8).

[0013] Further, adhesion between the compressor cylindrical surface sealing member and a compressor component having a cylindrical surface such as the housing or the pipe connector or the pressure control valve is performed by vulcanization adhesion of a rubber material. You can do this (claim 9).

The invention's effect

Therefore, in the present invention, since the axial dimension is longer than the diameter dimension of the annular portion of the O-ring when the O-ring is used, one of the axial directions in the compressor is on the high-pressure side and the other is the other. When intervening in the direction of the pressure difference from the low pressure side, the CO refrigerant

2 Since the permeability can be reduced, the amount of CO refrigerant leakage into the atmosphere outside the compressor or into the adjacent space can be relatively reduced. As a result, the phase of the sealing mechanism

2

Therefore, the complication and enlargement of the compressor are not caused, and the enlargement of the compressor can be prevented. In addition, since the seal mechanism can be handled by a single cylindrical seal member for a compressor having a simple structure, the compressor parts can be compared with the case where a seal mechanism having a plurality of compressor seal shaft members is used. It is possible to reduce the number of points and the manufacturing cost.

[0015] In particular, according to the invention of claim 2 or 3, the opening force abuts against the radially extending extension portion of the compressor and the housing of the compressor, or the opening force Since the extending portion extending inward and the surface of the compressor component mounted in the cylindrical seal member for the compressor abuts, it is possible to easily achieve proper positioning during the fastening operation, and to improve work efficiency. Optimization can be achieved. According to the invention described in claim 2, this force is also reduced. It is possible to prevent the cylindrical portion sealing member for a compressor from being displaced when incorporated. In particular, according to the invention described in claim 4, the mounting work of the compressor cylindrical surface sealing member to the compressor housing during the assembly of the compressor is simplified, and the inner periphery of the housing is locally installed after the mounting. Since the surface pressure between the surface and the outer peripheral surface of the cylindrical surface seal member for the compressor can be increased, the gap force between the nozzle and udging and the cylindrical surface seal member for the compressor is more likely to cause refrigerant leakage. It becomes possible to reduce effectively

[0016] In particular, according to the inventions of claims 5 and 6, even when hydrogenated-tolyl rubber is used as the main component of the elastomer material of the cylindrical surface sealing member for a compressor, the permeability of the CO refrigerant is low.

2

The reduction can be dealt with by improving the structure of the cylindrical seal member for compressors.- It is possible to relatively reduce the trityl content, thereby improving compression set at low temperatures. can do. In particular, according to the invention of claim 7, the heat resistance performance of the compressor cylindrical surface sealing member can be improved, and the compressor cylindrical surface sealing member according to the present invention can be obtained even in a high temperature environment of 150 degrees Celsius or higher. It can be used. Further, according to the invention described in claim 7, since the thermal conductivity of the cylindrical seal member for the compressor is significantly smaller than that of the metal housing compressor component, the compressor of the present invention having a large seal area. The cylindrical surface sealing member can be provided with a heat insulating function.

[0017] In particular, according to the invention of claim 9, the compressor cylindrical structure sealing member is a compressor, such as a housing, a partition member constituting the inner peripheral surface of the cylinder bore, a pipe connector, or a pressure control valve. Since it is directly bonded to the parts, there is no need for parts to connect them, so the number of parts can be reduced.

Brief Description of Drawings

FIG. 1 is a cross-sectional view showing an overall configuration of an example of a compressor in which the present invention is used.

[FIG. 2] FIG. 2 (a) is an enlarged cross-sectional view of the main part showing a state in which the above cylindrical surface sealing member is interposed between the hole of the rear head and the pipe connector, and FIG. 2 (a) is an explanatory view showing a configuration of a cylindrical surface sealing member, and FIG. 2 (c) is a cross-sectional view taken along the line II of FIG. 2 (b).

[FIG. 3] FIG. 3 (a) is an explanatory view showing a modification of the cylindrical surface sealing member of FIG. 2 (b) in which irregularities extending in the circumferential direction are formed on the outer peripheral surface on the side thereof. (b) shows II-II in Fig. 3 (a). It is line sectional drawing.

[FIG. 4] FIG. 4 (a) shows a cylindrical surface sealing member according to a modification having a projecting portion extending outward in the axial direction of the opening force relative to the cylindrical surface sealing member shown in FIG. FIG. 4 (b) is an explanatory view showing the configuration of the cylindrical surface sealing member of FIG. 4 (a), and FIG. Fig. 4 (b) is a sectional view taken along line III-III.

[FIG. 5] FIG. 5 (a) shows a cylindrical surface sealing member according to a modification having a projecting portion extending inward in the axial direction of the opening force with respect to the cylindrical surface sealing member shown in FIG. 2 and FIG. FIG. 5B is an enlarged cross-sectional view of a main part showing a state of being interposed between the connector and FIG. 5B is an explanatory view showing the configuration of the cylindrical surface sealing member of FIG. ) Is a cross-sectional view taken along line IV-IV in Fig. 5 (b).

Explanation of symbols

1 Compressor

2 Housing

4 Front head

5 rear head,

6 Drive shaft

10 Thrust flange

11 Cylinder bore

12 Single-headed piston (piston)

22 Swash plate (drive mechanism)

25 Support shaft (drive mechanism)

26 Long hole (drive mechanism)

35 Pressure control valve (compressor component)

38 Piping connector (compressor component)

55 Cylindrical seal member (cylindrical seal member for compressors)

55a opening 58 Extension

59 Extension part

60 Thrust bearing

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

In FIG. 1, a piston reciprocating variable capacity compressor 1 is shown as an example of the compressor 1 to which the present invention is used. The compressor 1 is, for example, carbon dioxide (CO 2)

Part of the refrigeration cycle using 2 as a refrigerant. That is, the compressor 1 compresses the low-temperature and low-pressure CO refrigerant by an evaporator (not shown) to increase the temperature and pressure,

2

The CO refrigerant is not shown, but it serves to send it out to the cooler.

2

[0022] The configuration of the compressor 1 will be described. The cylinder block 3, the front head 4 fixed to the front side of the cylinder block 3, and the rear side of the cylinder block 3 (right side in FIG. 1). A rear head 5 to be assembled and a drive shaft 6 are provided. The cylinder block 3, the front head 4, and the rear head 5 are joined to each other by passing fastening bolts 7 along the axial direction of a cylinder bore 11 to be described later. By fixing it, a metal-made, generally cylindrical, nozzle 2 is constructed.

A crank chamber 8 is defined by the front head 4 and the cylinder block 3. The crank chamber 8 houses a drive shaft 6 having one end protruding from the front head 4. The drive shaft 6 is provided so as to pass through a boss portion 4a that protrudes outward from the center portion of the front head 4, and a portion that protrudes from the boss portion 4a of the front head 4 is bolted to A pulley 14 fixed in the axial direction of the drive shaft 6 is rotatably fitted to the boss 4a via a bearing 15! RU

[0024] Further, the front end side of the drive shaft 6 is hermetically sealed with the front head 4 via a shaft sealing device 16 provided between the front shaft 4 and the outer peripheral surface. A radial bearing 17 is rotatably supported on the thrust flange 10 and the front head 4. The thrust flange 10 supports the thrust position of the drive shaft 6 via the thrust bearing 60, and is mounted on the front head 4 together with the radial bearing 17 included therein. In this configuration, the inner diameter of the thrust bearing 60 is smaller than the outer diameter of the radial bearing 17, so Although the rolling surface of the thrust bearing 17 cannot be formed directly on the relative surface of the front head 4, it is not necessary to use the thrust bearing 60 with a large outer diameter by using the thrust flange 10, and therefore the compressor. Preventing the increase in size and cost of 1. The rear end side of the drive shaft 6 is rotatably supported via a radial bearing 19 accommodated in the support recess 18 of the cylinder block 3. The shaft seal device 16 is not particularly shown, but a mechanism using a mechanical seal or a lip seal is used.

The cylinder block 3 is formed with the support recess 18 that supports the drive shaft 6 and a plurality of cylinder bores 11 that are arranged at equal intervals on the circumference around the support recess 18. A single-head piston 12 is inserted into each cylinder bore 11 so as to be able to reciprocate.

The swash plate 22 is formed in a cylindrical shape having a predetermined thickness, and a support shaft 25 inserted in a long hole 26 formed in the drive shaft 6 so as to be long in the axial direction of the drive shaft 6. The pin 20 protruding from the drive shaft 6 is engaged with the longitudinal groove 28 of the swash plate 22 so that the drive shaft 6 rotates integrally with the rotation of the drive shaft 6. It has become. A tail portion 12a of a single-headed piston 12 projecting into the crank chamber 8 through a pair of bushes 23 is moored on the peripheral portion of the swash plate 22.

Accordingly, assuming that the rotational movement of the drive shaft 6 is converted into the compression action of the refrigerant, when the drive shaft 6 rotates, the swash plate 22 rotates in synchronism with this, and this rotational motion is reduced to the shear 23. The reciprocating linear motion of the single-headed piston 12 is changed via the, and the volume of the compression chamber 24 formed between the piston 12 and the valve plate 9 in the cylinder bore 11 is changed by the reciprocating motion of the single-headed piston 12. It has become. The support shaft 25 that supports the swash plate 22 is urged in the direction of the cylinder block 3 by a spring 27.

The rear head 5 is joined to the cylinder block 3 via the valve plate 9, thereby defining a suction chamber 29 and a discharge chamber 30 formed continuously around the suction chamber 29. . The valve plate 9 has a suction hole 31 that communicates the suction chamber 29 and the compression chamber 24 via a suction valve (not shown), and a discharge that communicates the discharge chamber 30 and the compression chamber 24 via a suction valve (not shown). A hole 32 is formed.

In addition, the rear head 5 is provided with a mounting hole 34 on the side peripheral surface to control the pressure in the crank chamber 8. A pressure control valve 35 is mounted, and an annular projecting portion 36 projecting in the radial direction of the cylinder bore 11 is provided on the front head 4 side with respect to the mounting hole 34, and a pipe connector 38 is provided in the hole 37 of the projecting portion 36. Is to be installed. A discharge pressure side connection passage 41 connected to the discharge pressure side, a crank chamber connection passage 42 connected to the crank chamber 8, and a suction pressure side connection passage 43 connected to the suction chamber 29 are connected to the pressure control valve 35. By controlling the crank chamber pressure by the pressure control valve 35, the piston stroke, that is, the discharge capacity is adjusted.

In addition, the rear head 5 is provided with a centrifuge 44 that separates oil mixed in the discharged refrigerant gas discharged into the discharge chamber 30. The centrifuge 44 includes an oil separation chamber 45 in the discharge channel 40 from the discharge chamber 30. The oil separation chamber 45 defines a space that communicates with the hole 37 and extends in the axial direction of the hole 37, and a separation cylinder 46 having a smaller radial width than the space in the side of the hole 37 is inserted into the space. Defined.

The rear head 5 is defined by the oil reservoir chamber 47 being joined to the inside of the suction chamber 29 via the cylinder block 3 and the valve plate 9. The oil reservoir chamber 47 accommodates a bolt 48 for joining and fixing the cylinder block 3 and the valve plate 9, and the bolt 48 has a through hole 48 a formed as a throttle along its axial direction. The one end side opening of the through hole 48 a communicates with an isolation space 50 surrounded by the support recess 18, the rear end of the drive shaft 6, and the radial bearing 19. The oil reservoir chamber 47 communicates with the oil separation chamber 45 via the lubricating oil passage 51.

Thus, the discharged refrigerant gas is introduced from the discharge chamber 30 into the oil separation chamber 45 through the discharge flow path 40, and the introduced refrigerant gas turns around the separation cylinder 46 while being centered in the rear head 5. In the process, the lubricating oil mixed in the refrigerant gas is separated. The refrigerant gas from which the lubricating oil has been separated passes through the inside of the separation cylinder 46 and is sent out from the pipe connector 38, and the separated lubricating oil reaches the oil reservoir chamber 47 from the lubricating oil flow path 51, where it temporarily Then, when passing through the through hole 48a of the bolt 48, the pressure is reduced by the squeezing action to reach the isolation space 50, and further supplied to the shaft seal device 16 and the radial bearings 17 and 19.

In this embodiment, the front head 4 and the cylinder block 3 are the cylinder block 3. It is assumed to be exposed on the outer surface of the housing 2, and a sealing member 53 such as an O-ring is interposed on the surface where the front head 4 and the cylinder block 3 are in contact with each other to provide a good airtight seal. In addition, a sealing member 53 such as an O-ring is interposed on the surface where the cylinder block 3 and the valve plate 9 are in contact with each other to provide a good airtight seal. Further, a sealing member 53 such as an O-ring is interposed on the surface where the valve plate 9 and the rear head 5 are in contact with each other to provide a good airtight seal.

By the way, in this embodiment, a cylindrical surface seal is required between the housing 2 and the compressor component, one of which is in the direction of the pressure difference from the high pressure side and the other to the low pressure side (example) For example, between cylinder block 3 and front head 4 shown by arrow A in FIG. 1, between rear head 5 and piping connector 38 shown by arrow B in FIG. 1, and from rear head 5 and pressure shown by arrow C in FIG. A cylindrical surface sealing member 55 is interposed between the control valve 35 and the like.

[0035] As an example, the position indicated by the arrow B will be described with reference to FIG. A cylindrical surface sealing member 55 according to the present invention is interposed between the connector 38 and the connector 38. The cylindrical surface sealing member 55 is a cylindrical body having openings 55a on both sides in the axial direction as shown in FIG. 2 (b), and along the axial direction as shown in FIG. 2 (c). The dimension L1 is larger than the wall thickness dimension L2 on the side surface. Under these conditions, the dimension value of L1 is 2 mm to 20 mm, and the dimension value of L2 is 0.5 mm to 3 mm. It is preferable that

[0036] However, the cylindrical surface sealing member 55 has an axial dimension that is relatively longer than the diameter dimension of the annular portion of the O-ring when the O-ring is used. When the pressure difference is interposed between the inner peripheral surface of the hole 37 and the pipe connector 38, the permeability of the CO refrigerant can be made smaller than that of the O-ring. Member 55

2

The amount of leakage of CO refrigerant to the outside of the compressor 1 by passing through the

2

Can be reduced. As a result, the relative complexity and size of the seal mechanism are not increased, and the size of the compressor 1 can be prevented from increasing. In addition, since the cylindrical surface seal member 55 has a simple structure, the number of parts of the compressor 1 and the manufacturing cost can be reduced as compared with the case where a seal mechanism having a plurality of compressor seal shaft member forces is used. Can do. [0037] Then, the cylindrical surface sealing member 55 has a compression function in order to ensure a sealing function when it is interposed, and at the same time to prevent a compression set from becoming high due to high compression and shortening its life. The rate is 20% to 70%, for example, and a material that enables this compression rate is appropriately selected. That is, the material is made of, for example, an elastomer material strength mainly composed of hydrogenated-tolyl rubber, and in this case, the -tolyl content of hydrogenated-tolyl rubber does not exceed 45%. This reduces CO refrigerant permeation even when hydrogenated-tolyl rubber is used as the main component of the elastomer material of the cylindrical surface seal member 55.

2

Since this can be dealt with by improving the structure of the cylindrical surface sealing member 55, the nitrile content can be made relatively small, and the compression set at a low temperature can be improved. On the other hand, the cylindrical surface sealing member 55 may be made of an elastomer material force mainly composed of, for example, silicon rubber. Thereby, the heat resistance performance of the cylindrical surface sealing member 55 can be improved, and the cylindrical surface sealing member 55 can be used even in a high temperature environment of 150 degrees Celsius or higher. Since the cylindrical surface seal member 55 is formed of an elastomer material in this way, the thermal conductivity of the cylindrical surface seal member 55 becomes significantly smaller than that of the metal rear head 5 and the pipe connector 38. A large cylindrical surface seal member 55 can be provided with a heat insulating function by the rear head 5 and the pipe connector 38.

[0038] Further, in connecting the cylindrical surface sealing member 55 to the rear head 5 or the pipe connector 38 (only the connection to the pipe connector 38 is shown in Fig. 2 (a)), the rubber material 56 is bonded by vulcanization. You may make it go. This eliminates the need for parts for connecting the cylindrical surface sealing member 55 to the rear head 5 or the pipe connector 38, thereby reducing the number of parts.

Furthermore, as shown in FIGS. 3 (a) and 3 (b), the cylindrical surface sealing member 55 is formed with a plurality of convex portions 57 extending in the circumferential direction on the outer peripheral surface thereof. It may be pleated. Even in this case, it is the cylindrical portion that functions as a seal. Therefore, the mounting work of the cylindrical surface sealing member 55 into the hole 37 of the protrusion 36 is simplified, and the inner peripheral surface of the hole 37 is locally attached after mounting. Since the surface pressure with the outer peripheral surface of the cylindrical surface seal member 55 can be increased, the gap force between the inner peripheral surface of the hole 37 and the cylindrical surface seal member 55 can be more effectively reduced from causing refrigerant leakage. Is possible.

4 and 5 show another embodiment of the cylindrical surface sealing member 55 according to the present invention. Has been. Hereinafter, each cylindrical surface sealing member 55 will be described. However, the basic structure (including L1 and L2 dimensions), material, and the effects of the structure and material force of this cylindrical surface seal member 55 are the same as those described so far. The description will be omitted, and only different points will be described below.

[0041] The cylindrical surface sealing member 55 shown in FIG. 4 has a flange-like extending portion extending radially outward from the opening 55a, as shown particularly in FIGS. 4 (b) and 4 (c). It is the one with 58. As a result, as shown in FIG. 4 (a), when the cylindrical surface sealing member 55 is mounted in the hole 37, the extended portion 58 abuts against the peripheral portion of the opening of the hole 37 and the cylindrical surface sealing member is further removed. Since 55 is prevented from entering the hole 37, proper positioning can be easily achieved during work, and work efficiency can be optimized.

[0042] The cylindrical surface sealing member 55 shown in FIG. 5 is adapted to restrict the opening 55a radially inward from the opening 55a as shown in FIGS. 5 (b) and 5 (c). It has an extension 59 that extends to the front. As a result, as shown in FIG. 5 (a), when the piping connector 38 is mounted in the cylindrical surface sealing member 55, the distal end surface of the piping connector 38 abuts against the surface of the extended portion 59 so that the piping connector 38 Can be prevented from penetrating the cylindrical surface sealing member 55, so that proper positioning can be easily achieved at the time of work, and work efficiency can be optimized.

Note that the cylindrical surface sealing member 55 shown in FIGS. 4 and 5 is not particularly shown, but a convex portion extending in the circumferential direction as shown in FIG. 57 may be formed into a plurality of pleats.

Also, a cylindrical surface seal member 55 interposed between the front head 4 and the cylinder block 3 indicated by arrow A and a cylindrical surface seal interposed between the rear head 5 indicated by arrow C and the pressure control valve 35. The member 55 having the structure shown in FIGS. 2 to 5 is also used, and the dimensional values (Ll, L2), materials, and the like are the same, and thus the description thereof is omitted.

[0045] Finally, the compressor to which the present invention is used has been described as a piston reciprocating capacity variable type compressor 1 with reference to FIG. 1, but is not necessarily limited to this type of compressor. The cylindrical surface sealing member 55 only needs to be interposed between the housing and the compressor component, so that the present invention can be used for any compressor. wear. That is, for a compressor such as an electric compressor, it is possible to prevent leakage of refrigerant from the fastening portion by applying the cylindrical surface sealing member 55 described above to the compressor component.

Claims

The scope of the claims

[1] A compressor having a housing, a drive shaft rotatably supported by the housing and rotated by an external driving force, and a drive mechanism for converting the rotation of the drive shaft into a refrigerant compression action In

When fastening a compressor component having a cylindrical surface such as the piping connector or a pressure control valve to the housing, between the housing and a compressor component having a cylindrical surface such as the piping connector or a pressure control valve. In addition, a cylindrical surface sealing member for a compressor having a cylindrical body open on both sides in the axial direction, the dimension along the axial direction being larger than the wall thickness of the side surface, The refrigerant leakage prevention structure from the fastening part of the compressor component, characterized in that is installed so that the pressure difference is in the direction of the pressure difference from the low pressure side.

[2] The refrigerant leakage from the fastening part of the compressor component according to claim 1, wherein the cylindrical surface sealing member for the compressor has an extending portion that extends outward in the radial direction of the opening force. Prevention structure.

[3] The refrigerant leakage from the fastening part of the compressor component according to claim 1, wherein the cylindrical surface sealing member for the compressor has an extension portion extending radially inward of the opening force. Prevention structure.

[4] The compressor configuration according to claim 1, 2, or 3, wherein the cylindrical surface sealing member for a compressor has a plurality of convex portions on the outer peripheral surface of the cylindrical body so as to have a pleat shape. Structure to prevent refrigerant leakage from the fastening part of the part.

[5] The fastening part of the compressor component according to claim 1, 2, 3, or 4, wherein the cylindrical surface sealing member for a compressor is made of an elastomer material mainly composed of hydrogenated-tolyl rubber. Refrigerant leakage prevention structure.

[6] The elastomer material forming the cylindrical seal member for a compressor has a tolyl content of the hydrogenated tolyl rubber in a range not exceeding 45%. Refrigerant leakage prevention structure from the fastening part of the compressor components.

[7] The compressor cylindrical surface sealing member is made of an elastomer material mainly composed of silicone rubber, from the fastening portion of the compressor component according to claim 1, 2, 3 or 4 Refrigerant leakage prevention structure.

[8] The cylindrical surface sealing member for a compressor is characterized in that a dimension along the axial direction is 2 mm to 20 mm, and a wall thickness dimension of a side portion is 0.5 mm to 3 mm. The refrigerant leakage prevention structure from the fastening site | part of the compressor component in any one of from 7 to 7.

[9] Adhesion between the compressor cylindrical surface sealing member and the compressor component having a cylindrical surface such as the housing or the pipe connector or the pressure control valve is performed by vulcanization adhesion of a rubber material. The structure for preventing refrigerant leakage from the fastening portion of the compressor component according to any one of claims 1 to 8.