Compressor

Abstract

To provide a compressor capable of maintaining sealing performance at a low temperature.SOLUTION: A compressor includes: a cylindrical motor case 110 surrounding a compression mechanism 200 around an axis X; a lower case 130 closing an opening 111 of the motor case 110 and fitted to an inner peripheral surface of the motor case 110 to define an accommodation chamber C1 to which a refrigerant is introduced between the lower case and the motor case 110; a first O-ring 151 provided around the axis X at an opposing portion where the surfaces of the motor case 110 and the lower case 130 fitted to each other oppose to each other; and a second O-ring 152 provided around the axis X at the opposing portion. The first O-ring 151 is provided at a position nearer to a starting point on the accommodation chamber C1 side of the opposing portion, relative to the second O-ring 152. Refrigerant resistance and / or oil resistance of the first O-ring 151 is superior to that of the second O-ring 152, and sealing performance of the second O-ring 152 is superior to that of the first O-ring 151 at a temperature of -20°C or lower.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present disclosure relates to a compressor. [Background technology]

[0002] In an electric compressor in which one casing is composed of a plurality of cases, a sealing member such as an O-ring may be provided between one case and another case to ensure sealing between the cases. For example, in Patent Document 1, two O-rings are provided between one case and another case, and are arranged side by side in the axial direction. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 2020-143650 Summary of the Invention [Problem to be solved by the invention]

[0004] Sealing members placed in positions where they are likely to come into contact with the refrigerant are required to be refrigerant-resistant and / or oil-resistant, but some sealing members that meet these requirements lose their sealing ability at low temperatures (for example, when exposed to a temperature environment of -20°C or below).

[0005] The present disclosure has been made in view of the above circumstances, and has an object to provide a compressor that can maintain sealing performance even at low temperatures. [Means for solving the problem]

[0006] In order to solve the above problems, the compressor of the present disclosure employs the following measures. That is, a compressor according to one embodiment of the present disclosure comprises a cylindrical main case that surrounds a compression mechanism that compresses a refrigerant around an axis; a sub-case that closes an opening of the main case in the axial direction and is fitted to the inner or outer peripheral surface of the main case to define a space into which a refrigerant is introduced between the main case and a sub-case; an annular first sealing member that is provided around the axis at an opposing location where the fitted main case and sub-case face each other; and an annular second sealing member that is provided around the axis at the opposing location, wherein the first sealing member is provided at a position closer to the starting point of the opposing location on the space side than the second sealing member, the first sealing member has better refrigerant resistance and / or oil resistance than the second sealing member, and the second sealing member has better sealing properties than the first sealing member at temperatures below -20°C. [Effects of the Invention]

[0007] According to the present disclosure, sealing performance can be maintained even at low temperatures. [Brief explanation of the drawings]

[0008] [Figure 1] 1 is a longitudinal cross-sectional view of a compressor according to one embodiment of the present disclosure. FIG. [Figure 2] FIG. 2 is a partial enlarged view of part A shown in FIG. [Figure 3] This is a first modification of part A shown in FIG. [Figure 4] This is a second modification of part A shown in FIG. [Figure 5] This is a third modification of part A shown in FIG. DETAILED DESCRIPTION OF THE INVENTION

[0009] Hereinafter, a compressor according to an embodiment of the present disclosure will be described with reference to the drawings.

[0010] [Compressor overview] The compressor 10 is a device that compresses a refrigerant (for example, R1234yf) containing refrigeration oil (for example, POE oil). In the following description, the compressor 10 is exemplified as a scroll compressor in which the compression mechanism 200 and the electric motor 400 serving as the drive unit are housed in the internal space of the casing 100, which is an enclosed space; however, the compressor may also be a so-called open scroll compressor in which the drive unit is located outside the enclosed space.

[0011] As shown in FIG. 1, the compressor 10 includes a casing 100, a compression mechanism 200, a crankshaft 310, and an electric motor 400.

[0012] The casing 100 has a motor case (main case) 110, an upper case 120, and a lower case (sub-case) .

[0013] The motor case 110 is a cylindrical member that extends along the direction of the axis X and is open at both ends. The motor case 110 surrounds the compression mechanism 200, the crankshaft 310, and the electric motor 400 around the X-axis.

[0014] The upper case 120 is a member that closes one opening of the motor case 110 . The upper case 120 is fixed to the motor case 110 with bolts 530 .

[0015] The lower case 130 is a member that closes the other opening of the motor case 110 (hereinafter referred to as "opening 111"). The lower case 130 is fixed to the motor case 110 with bolts (not shown). The detailed configuration of the portion where the motor case 110 and the lower case 130 are fitted together will be described later. An inverter cover 140 is attached to the lower case 130 with screws 540. In the space defined by the lower case 130 and the inverter cover 140, an inverter (not shown) is housed.

[0016] The sealed space defined by the casing 100 (motor case 110, upper case 120, and lower case 130) configured as described above accommodates the compression mechanism 200, crankshaft 310, electric motor 400, and various other components.

[0017] The compression mechanism 200 is a mechanism that compresses low-pressure gas refrigerant taken in from the outside of the casing 100 via the suction port 116 . The compression mechanism 200 includes a fixed scroll 210 and an orbiting scroll 220 .

[0018] The fixed scroll 210 is a member having a fixed end plate and a spiral-shaped fixed side wall body standing upright from the end plate. The fixed scroll 210 is fixed to the upper case 120 with bolts 550. The outer peripheral surface of the fixed end plate of the fixed scroll 210 is in contact with the inner peripheral surfaces of the motor case 110 and the upper case 120 while maintaining a seal. This divides the sealed space inside the casing 100 into an accommodation chamber C1 defined by the fixed scroll 210, motor case 110, and lower case 130, and a discharge chamber C2 defined by the fixed scroll 210 and upper case 120. The sealing between the fixed scroll 210 and the motor case 110 and the sealing between the fixed scroll 210 and the upper case 120 are ensured by, for example, O-rings.

[0019] The orbiting scroll 220 is a member having an orbiting-side end plate and a spiral-shaped orbiting-side wall body standing upright from the end plate. The orbiting scroll 220 is configured to revolve around the fixed scroll 210 by means of a crankshaft 310 that rotates around the axis X (more specifically, a crankpin 312 that revolves around the axis X) and a known anti-rotation mechanism.

[0020] The fixed scroll 210 and the orbiting scroll 220 have their respective wall bodies meshed with each other to form a compression chamber C3.

[0021] The crankshaft 310 is a member for transmitting driving force from the electric motor 400 to the orbiting scroll 220 . The crankshaft 310 has a shaft body 311 and a crank pin 312 .

[0022] Shaft body 311 is a shaft-shaped member extending along axis X. Shaft body 311 is driven to rotate around axis X by electric motor 400. The shaft body 311 is supported so as to be freely rotatable around the axis X by a main bearing 510 arranged on the upper case 120 side and fixed to the motor case 110, and a sub-bearing 520 arranged on the lower case 130 side and fixed to the lower case 130.

[0023] Crank pin 312 is a shaft-shaped member provided at the end of shaft body 311 on the upper case 120 side. Crank pin 312 extends along another axis that is eccentric with respect to axis X. As a result, when shaft body 311 rotates around axis X, crank pin 312 revolves around axis X. The crank pin 312 is connected to a boss portion 221 formed on the orbiting scroll 220 via a bearing 222 .

[0024] The compressor 10 configured as above is driven as follows. That is, when the shaft body 311 of the crankshaft 310 is driven to rotate around the axis X by the electric motor 400, the orbiting scroll 220 connected to the crank pin 312 is driven. The gas refrigerant taken into the storage chamber C1 on the lower case 130 side through the suction port 116 is guided to the storage chamber C1 on the compression mechanism 200 side through a refrigerant passage formed between the inner surface of the motor case 110 and the outer surface of the electric motor 400 (stator). The refrigerant introduced into the accommodation chamber C1 on the compression mechanism 200 side is drawn into the compression chamber C3. At this time, the volume of the compression chamber C3 is gradually reduced by the orbital motion of the orbiting scroll 220, so that the gas refrigerant is compressed accordingly. The compressed high-temperature, high-pressure gas refrigerant is guided to the discharge chamber C2 via a discharge port 211a formed substantially in the center of the fixed-side end plate of the fixed scroll 210 and a discharge valve (not shown) provided at the outlet of the discharge port 211a. The gas refrigerant introduced into the discharge chamber C2 is discharged to the outside of the compressor 10 via a discharge port (not shown) provided in the upper case 120.

[0025] [Regarding the fitting between the motor case and lower case] As shown in FIGS. 1 and 2, the lower case 130 is formed with an annular protrusion 131. The annular protrusion 131 is a portion formed on the lower case 130 facing the opening 111 of the motor case 110 . The annular protrusion 131 protrudes along the direction of the axis X and is formed in an annular shape around the axis X, and is fitted into the inner circumferential surface of the opening 111. In other words, the outer diameter of the annular protrusion 131 corresponds to the inner diameter of the opening 111.

[0026] When the motor case 110 and the lower case 130 are fitted together, two sealing members (a first O-ring 151 and a second O-ring 152) are provided in the area where the motor case 110 and the lower case 130 face each other, more specifically, in the area where the portion of the motor case 110 on the opening 111 side faces the annular protrusion 131 of the lower case 130 face each other (hereinafter referred to as the "facing area L").

[0027] The first O-ring 151 is a sealing member having rubber elasticity and formed in an annular shape around the axis X. The second O-ring 152 is a sealing member having rubber elasticity and formed in an annular shape around the axis X. However, the first O-ring 151 and the second O-ring 152 are made of different materials, as will be described in detail later.

[0028] The first O-ring 151 is provided, for example, in a first annular groove 133 formed in the outer peripheral surface of the annular protrusion 131. The second O-ring 152 is provided, for example, in a second annular groove 134 formed in the outer peripheral surface of the annular protrusion 131. When assembled to the compressor 10, the first O-ring 151 and the second O-ring 152 are in close contact with the motor case 110 and the lower case 130, respectively, and are compressed and crushed between the motor case 110 and the lower case 130.

[0029] Here, the first annular groove 133 is formed at a position closer to the start point Ls of the opposing portion L (a position farther away from the end point Le of the opposing portion L) than the second annular groove 134. In other words, the first O-ring 151 is provided at a position closer to the start point Ls of the opposing portion L (a position farther away from the end point Le of the opposing portion L) than the second O-ring 152. Here, the start point Ls of the facing point L is a point (portion) of the facing point L that is adjacent to the accommodation chamber C1 and contacts the exterior of the compressor 10. The end point Le of the facing point L is a point (portion) of the facing point L that is adjacent to the accommodation chamber C1 and contacts the exterior of the compressor 10.

[0030] 2, the starting point Ls of the opposing portion L is located on the side of the end face 131a of the annular convex portion 131. In other words, the first annular groove 133 is formed at a position closer to the end face 131a of the annular convex portion 131 than the second annular groove 134.

[0031] With this arrangement, if the gas refrigerant infiltrates from the accommodation chamber C1 along the opposing location L via the starting point Ls, the refrigerant will first come into contact with the first O-ring 151. Only if the gas refrigerant passes between the first O-ring 151 and the inner circumferential surface of the motor case 110 will the refrigerant come into contact with the second O-ring 152.

[0032] Here, the first O-ring 151 has better refrigerant resistance and / or oil resistance than the second O-ring 152. The second O-ring 152 has better sealing properties than the first O-ring 151 at temperatures below -20°C, for example.

[0033] The refrigerant resistance is evaluated by, for example, an immersion test using a refrigerant (R1234yf) (JIS K 6258, "Vulcanized rubber and thermoplastic rubber -- Determination of liquid resistance"). In addition to the immersion test, refrigerant resistance is evaluated by a foaming test, in which the O-ring is immersed in the refrigerant, then heated with air, and the O-ring is cut in 10 places to check for cracks in the cross section.

[0034] The oil resistance is evaluated by, for example, an immersion test using refrigerating machine oil (POE oil) (JIS K 6258, "Vulcanized rubber and thermoplastic rubber -- Determination of liquid resistance").

[0035] Sealing ability is evaluated, for example, by the TR test (JIS K 6261, "Vulcanized rubber and thermoplastic rubber - Determination of low-temperature properties"). Specifically, it is evaluated by the TR10 value (the temperature at which the shrinkage rate is 10%). The lower this temperature, the better the sealing ability at low temperatures. Note that if an O-ring is used at a temperature lower than the TR10 value, the rubber elasticity of the O-ring may decrease, making it impossible to ensure sealing ability.

[0036] An example of the material for the first O-ring 151 selected through the above evaluation is HNRB, and an example of the material for the second O-ring 152 is EPDM.

[0037] By making the first O-ring 151 and the second O-ring 152 different colors, the first O-ring 151 and the second O-ring 152 can be easily distinguished visually. This prevents the O-rings from being assembled incorrectly.

[0038] According to this embodiment, the following effects are achieved. The motor case 110 and the lower case 130 are fitted together and the first O-ring 151 is provided around the axis X at an opposing position L where the faces of the fitted motor case 110 and the lower case 130 face each other, and the second O-ring 152 is provided around the axis X at the opposing position L. The first O-ring 151 is provided at a position closer to a start point Ls of the opposing position L than the second O-ring 152. The first O-ring 151 has better refrigerant resistance and / or oil resistance than the second O-ring 152, and the second O-ring 152 has better refrigerant resistance and / or oil resistance than the first O-ring 151 at temperatures of -20°C or lower. Because of their excellent sealing properties, even when the first O-ring 151 and the second O-ring 152 are exposed to temperatures below −20° C. during operation of the compressor 10, the first O-ring 151, which is located in a position where it is likely to come into contact with the refrigerant, can maintain a certain level of sealing performance while suppressing deterioration due to the refrigerant (including lubricating oil) due to its excellent refrigerant resistance and / or oil resistance. The second O-ring 152 can maintain high sealing performance even in a temperature environment of −20° C. Although the second O-ring 152 has inferior refrigerant resistance and / or oil resistance to the first O-ring 151, it is less susceptible to deterioration due to the refrigerant (is less susceptible to the effects of the refrigerant). This is because only a small amount of refrigerant passes through the first O-ring 151, which has inferior sealing performance at low temperatures compared to the second O-ring 152 but has excellent refrigerant resistance and / or oil resistance and maintains a certain level of sealing performance. This is because only a small amount of refrigerant may come into contact with the second O-ring 152. In this way, by combining the first O-ring 151 and the second O-ring 152 made of different materials, sealing performance can be maintained for a long period of time even at low temperatures.

[0039] Furthermore, by making the first O-ring 151 and the second O-ring 152 different colors, it is possible to prevent the O-rings from being assembled incorrectly.

[0040] [Variation 1] As shown in FIG. 3, a second O-ring 152 may be provided on an end surface 111 a of the opening 111 of the motor case 110 . In this case, a first annular groove 133 is formed on the outer peripheral surface of the annular protrusion 131, and a second annular groove 114 is formed on the end surface 111a of the opening 111 of the motor case 110.

[0041] [Variation 2] As shown in FIG. 4, the inner peripheral surface of the lower case 130 may be fitted onto the outer peripheral surface of the motor case 110. In this case, a first annular groove 113 and a second annular groove 114 are formed on the outer peripheral surface of the motor case 110 on the end face 111a side. Furthermore, the starting point Ls of the opposing portion L is located on the side of the end face 111a of the opening 111. Therefore, the first annular groove 133 is formed at a position closer to the end face 111a of the opening 111 than the second annular groove 134. In other words, the first O-ring 151 is provided at a position closer to the end face 111a of the opening 111 than the second O-ring 152.

[0042] [Variation 3] 5, the second O-ring 152 may be provided on a chamfered portion 111b connected to an end surface 111a of the motor case 110. The chamfered portion 111b is part of the inner circumferential surface of the motor case 110. In this case, a first annular groove 133 is formed on the outer peripheral surface of the annular protrusion 131, and the chamfered portion 111b corresponds to the second annular groove 114 or the second annular groove .

[0043] In any of the embodiments (including the modified examples), the part in which the annular groove in which the two O-rings are provided can be formed can be selected arbitrarily from the motor case 110 and the lower case 130. Alternatively, two annular grooves may be formed in the end face 111a of the motor case 110 and / or the surface of the lower case 130 facing the end face 111a, and two O-rings may be provided therein.

[0044] The compressor according to the present embodiment described above can be understood, for example, as follows. That is, a compressor (10) according to a first aspect of the present disclosure includes a cylindrical main case (110) surrounding a compression mechanism (200) that compresses a refrigerant around an axis (X); a sub-case (130) that closes an opening (111) of the main case in the direction of the axis and is fitted to an inner or outer circumferential surface of the main case to define a space (C1) into which a refrigerant is introduced between the main case and the sub-case; an annular first seal member (151) provided around the axis at an opposing position (L) where the fitted main case and the sub-case face each other; and an annular second seal member (152) provided around the axis at the opposing position, wherein the first seal member is provided at a position closer to a start point (Ls) of the opposing position on the space side than the second seal member, the first seal member having better refrigerant resistance and / or oil resistance than the second seal member, and the second seal member having better sealing performance than the first seal member at a temperature of −20° C. or lower.

[0045] The compressor according to this aspect includes a first annular seal member provided around the axis at the opposing location where the fitted main case and sub-case face each other, and a second annular seal member provided around the axis at the opposing location. The first seal member is provided closer to the start point of the opposing location on the space side than the second seal member. The first seal member has better refrigerant resistance and / or oil resistance than the second seal member, and the second seal member has better sealing performance than the first seal member at temperatures of -20°C or below. Therefore, even when the first and second seal members are exposed to an environment of temperatures of -20°C or below during operation of the compressor, the first seal member, which is provided in a location where it is likely to come into contact with the refrigerant, can ensure a certain level of sealing performance while suppressing deterioration due to the refrigerant (including lubricating oil) due to its excellent refrigerant resistance and / or oil resistance. Furthermore, the second seal member can ensure high sealing performance even in a temperature environment of -20°C due to its excellent low-temperature sealing performance. In this case, the second seal member is less refrigerant-resistant and / or oil-resistant than the first seal member, but is less susceptible to deterioration by the refrigerant (is less susceptible to the effects of the refrigerant). This is because only a small amount of refrigerant passes through the first seal member, which has a lower sealing performance at low temperatures than the second seal member but is superior in refrigerant-resistant and / or oil-resistant properties and exhibits a certain level of sealing performance. In other words, the amount of refrigerant that may come into contact with the second seal member is small. In this way, by combining the first seal member and the second seal member made of different materials, it is possible to maintain sealing performance even at low temperatures for a long period of time.

[0046] In addition, the compressor according to a second aspect of the present disclosure may be such that, in the first aspect, the first sealing member is arranged so as to contact the inner or outer peripheral surface of the main case, and the second sealing member is arranged so as to contact the inner or outer peripheral surface of the main case.

[0047] According to the compressor of this aspect, the first sealing member is arranged so as to contact the inner or outer peripheral surface of the main case, and the second sealing member is arranged so as to contact the inner or outer peripheral surface of the main case, so that sealing can be achieved by the inner or outer peripheral surface of the main case.

[0048] Furthermore, in the compressor according to a third aspect of the present disclosure, in the first aspect, the first sealing member may be arranged so as to contact the inner or outer peripheral surface of the main case, and the second sealing member may be arranged so as to contact the open end surface of the main case.

[0049] In the compressor of this aspect, the first sealing member is arranged so as to contact the inner or outer peripheral surface of the main case, and the second sealing member is arranged so as to contact the opening end face of the main case, so that sealing can be achieved by the inner or outer peripheral surface of the main case and the opening end face of the main case.

[0050] Furthermore, in the compressor according to a fourth aspect of the present disclosure, in the first aspect, the first seal member may be arranged so as to contact the opening end surface of the main case, and the second seal member may be arranged so as to contact the opening end surface of the main case.

[0051] According to the compressor of this aspect, the first sealing member is arranged so as to contact the opening end face of the main case, and the second sealing member is arranged so as to contact the opening end face of the main case, so that sealing can be achieved by the opening end face of the main case.

[0052] Further, in the compressor according to a fifth aspect of the present disclosure, in any one of the first to fourth aspects, the first seal member and the second seal member are different in color.

[0053] According to the compressor of this aspect, the first seal member and the second seal member are different in color, which makes it possible to prevent the seal members from being assembled incorrectly. [Explanation of symbols]

[0054] 10 Compressor 100 casing 110 Motor case (main case) 111 Aperture 111a End face 111b Chamfered part 113 First Annular Groove 114 Second annular groove 116 Intake port 120 Upper Case 130 Lower case (subcase) 131 Annular convex part 131a End face 133 First Circular Groove 134 Second annular groove 140 Inverter cover 151 First O-ring (first seal member) 152 Second O-ring (second seal member) 200 Compression Mechanism 210 Fixed Scroll 211a Discharge port 220 Rotating Scroll 221 Boss Department 222 Bearings 310 crankshaft 311 Shaft body 312 Crankpin 400 electric motor 510 Main bearing 520 Sub-bearing 530 Volts: for upper case 540 Screw: for inverter cover 550 Volts: for fixed scroll C1 Containment Cell C2 discharge chamber C3 compression chamber X axis

Claims

1. a cylindrical main case that surrounds a compression mechanism that compresses a refrigerant around an axis; a sub-case that closes an opening of the main case in the axial direction and is fitted to an inner circumferential surface or an outer circumferential surface of the main case to define, between the sub-case and the main case, a space into which a refrigerant is introduced; a first annular seal member provided around the axis at a location where the main case and the sub-case, which are fitted together, face each other; a second annular seal member provided around the axis at the opposing location; Equipped with the first seal member is provided at a position closer to a starting point of the opposing portion on the space side than the second seal member, the first seal member has better refrigerant resistance and / or oil resistance than the second seal member; The second seal member has better sealing properties than the first seal member at temperatures of -20°C or lower.

2. the first seal member is disposed so as to contact an inner circumferential surface or an outer circumferential surface of the main case, The compressor according to claim 1 , wherein the second seal member is disposed so as to contact an inner circumferential surface or an outer circumferential surface of the main case.

3. the first seal member is disposed so as to contact an inner circumferential surface or an outer circumferential surface of the main case, The compressor according to claim 1 , wherein the second seal member is disposed so as to contact an open end surface of the main case.

4. the first seal member is disposed so as to contact an open end surface of the main case, The compressor according to claim 1 , wherein the second seal member is disposed so as to contact an open end surface of the main case.

5. The compressor according to claim 1 , wherein the first seal member and the second seal member are different in color.

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