JP6841010B2 - Rotary compressor - Google Patents

Description

The present invention relates to a rotary compressor.

R410A refrigerant is widely used as the refrigerant in the refrigeration cycle apparatus including the compressor that compresses the refrigerant. Since the R410A refrigerant has a large global warming potential (GWP), a related technique using a refrigerant containing hydrofluoroolefin (HFO) 1123 (hereinafter referred to as HFO1123 refrigerant) as a refrigerant having a relatively small GWP has been developed. Are known.

International Publication No. 2014/057036

The above-mentioned HFO1123 refrigerant has a property of causing a disproportionation reaction when energy is applied under certain conditions. When a disproportionation reaction occurs in the refrigerant, a large amount of heat is generated. Therefore, if a disproportionation reaction occurs in the refrigeration cycle device, the operational reliability of the refrigeration cycle device including the compressor may be lowered, or a sudden pressure may be generated. There is a risk of damaging the refrigerant piping.

Further, in the rotary compressor, the compression portion is immersed in oil (lubricating oil) for ensuring the slidability of the piston in the cylinder for compressing the refrigerant and ensuring the airtightness of the compression chamber. In such a rotary compressor, when the compressor is stopped for a long time at a low outside air temperature, a large amount of refrigerant dissolves in the oil, that is, a so-called refrigerant stagnation phenomenon occurs. If the compressor is started while the refrigerant is laid down, liquid compression may occur in which the liquid refrigerant is compressed when the low-pressure side refrigerant in the refrigerant circulation path of the refrigeration cycle device is supplied into the rotary compressor. is there. In a rotary compressor using a refrigerant having a property of causing a disproportionation reaction as described above, when liquid compression occurs, the pressure of the refrigerant in the compression chamber may locally rise to, for example, about 30 Mpa. This high pressure may cause a disproportionation reaction in the refrigerant.

The disclosed technique has been made in view of the above, and an object of the present invention is to provide a rotary compressor capable of suppressing a disproportionation reaction of a refrigerant when liquid compression occurs.

One aspect of the rotary compressor disclosed in the present application is a vertically placed cylindrical compressor housing in which a refrigerant discharge portion is provided at an upper portion and a refrigerant suction portion is provided at a lower portion and is sealed, and inside the compressor housing. The compressor has a compression unit that is arranged at the lower part and compresses the refrigerant sucked from the suction part and discharges from the discharge part, and a motor that is arranged at the upper part in the compressor housing and drives the compression part. The portions include an annular cylinder, an upper end plate that closes the upper side of the cylinder, a lower end plate that closes the lower side of the cylinder, a rotating shaft having an eccentric portion and being rotated by the motor, and the eccentricity. A piston that is fitted into a portion and revolves along the inner peripheral surface of the cylinder to form a cylinder chamber in the cylinder, and a vane groove provided in the cylinder that protrudes into the cylinder chamber and the tip portion abuts on the piston. A vane that divides the cylinder chamber into a suction chamber and a compression chamber, a spring that is arranged on one end side of the vane groove and urges the vane to the cylinder chamber, one end side of the vane groove, and the compressor housing. In a rotary compressor having a pressure introduction path communicating with the inside of the body and a discharge hole for discharging the refrigerant compressed in the compression chamber from the compression chamber, the refrigerant is an HFO1123 refrigerant or a mixed refrigerant containing an HFO1123 refrigerant. When the second pressure in the compression chamber is larger than the first pressure in the pressure introduction path on one end side of the vane groove, the vane is attached to the tip of the vane. A predetermined gap is opened between the piston and the outer peripheral surface.

According to one aspect of the rotary compressor disclosed in the present application, it is possible to suppress the disproportionation reaction of the refrigerant when liquid compression occurs.

FIG. 1 is a vertical cross-sectional view showing a rotary compressor of an embodiment. FIG. 2 is an exploded perspective view showing a compression portion of the rotary compressor of the embodiment. FIG. 3 is a cross-sectional view of the compression portion of the rotary compressor of the embodiment as viewed from above. FIG. 4 describes a gap generated between the tip of the upper vane and the outer peripheral surface of the upper piston and a gap generated between the tip of the lower vane and the outer peripheral surface of the lower piston in the rotary compressor of the embodiment. It is a cross-sectional view for this purpose.

Hereinafter, examples of the rotary compressor disclosed in the present application will be described in detail with reference to the drawings. The rotary compressor disclosed in the present application is not limited by the following examples.

FIG. 1 is a vertical cross-sectional view showing a rotary compressor of an embodiment. FIG. 2 is an exploded perspective view showing a compression portion of the rotary compressor of the embodiment. FIG. 3 is a cross-sectional view of the compression portion of the rotary compressor of the embodiment as viewed from above.

As shown in FIG. 1, the rotary compressor 1 has a compression unit 12 arranged at the lower part in a sealed vertical cylindrical compressor housing 10 and a rotary compressor 1 arranged at the upper part inside the compressor housing 10 and rotates. A motor 11 for driving the compression unit 12 via a shaft 15 and a vertically placed cylindrical accumulator 25 fixed to and sealed on the outer peripheral surface of the compressor housing 10 are provided.

The accumulator 25 is connected to the upper cylinder chamber 130T (see FIG. 2) of the upper cylinder 121T via the upper suction pipe 105 as the suction part and the upper curved pipe 31T of the accumulator, and the lower suction pipe 104 as the suction part and the lower curved accumulator. It is connected to the lower cylinder chamber 130S (see FIG. 2) of the lower cylinder 121S via a pipe 31S. In this embodiment, the positions of the upper suction pipe 105 and the lower suction pipe 104 overlap each other in the circumferential direction of the compressor housing 10, and are located at the same position.

The motor 11 includes a stator 111 arranged on the outside and a rotor 112 arranged on the inside. The stator 111 is fixed to the inner peripheral surface of the compressor housing 10 in a shrink-fitted state. The rotor 112 is fixed to the rotating shaft 15 in a shrink-fitted state.

In the rotating shaft 15, the lower sub-shaft portion 151 of the lower eccentric portion 152S is rotatably supported by the sub-bearing portion 161S provided on the lower end plate 160S, and the upper spindle portion 153 of the upper eccentric portion 152T is at the upper end. It is rotatably supported by the main bearing portion 161T provided on the plate 160T. The rotating shaft 15 is provided with an upper eccentric portion 152T and a lower eccentric portion 152S with a phase difference of 180 degrees from each other, and an upper piston 125T is supported by the upper eccentric portion 152T and a lower eccentric portion 152S. The lower piston 125S is supported. As a result, the rotating shaft 15 is rotatably supported with respect to the entire compression portion 12, and the upper piston 125T is revolved along the inner peripheral surface of the upper cylinder 121T by rotation, and the lower piston 125S is moved to the lower cylinder 121S. Revolve along the inner peripheral surface of the.

Inside the compressor housing 10, the lubricity of the sliding portions such as the upper piston 125T and the lower piston 125S sliding in the compression portion 12 is ensured, and the upper compression chamber 133T (see FIG. 2) and the lower compression chamber 133S. In order to seal (see FIG. 2), the lubricating oil 18 is sealed in an amount that substantially immerses the compression portion 12. On the lower side of the compressor housing 10, mounting legs 310 (see FIG. 1) for locking a plurality of elastic support members (not shown) that support the entire rotary compressor 1 are fixed.

As shown in FIG. 2, the compression unit 12 compresses the refrigerant sucked from the upper suction pipe 105 and the lower suction pipe 104, and discharges the refrigerant from the discharge pipe 107 as a discharge unit described later. As shown in FIG. 2, the compression portion 12 has an upper end plate cover 170T, an upper end plate 160T, an annular upper cylinder 121T, an intermediate partition plate 140, and an annular shape having a bulging portion in which a hollow space is formed from above. The lower cylinder 121S, the lower end plate 160S, and the flat lower end plate cover 170S are laminated. The entire compression unit 12 is fixed by a plurality of through bolts 174, 175 and auxiliary bolts 176 arranged on substantially concentric circles from above and below. As shown in FIGS. 2 and 3, the lower end plate 160S, the lower end plate cover 170S, the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, the upper end plate 160T, and the upper end plate cover 170T have substantially the same phase positions on concentric circles. Is provided with a plurality of bolt through holes 137 through which the through bolts 174 and 175 and the auxiliary bolts 176 are passed.

As shown in FIG. 3, the upper cylinder 121T is formed with an upper cylinder inner wall 123T along a concentric circle with the rotating shaft 15 of the motor 11. An upper piston 125T having an outer diameter smaller than the inner diameter of the upper cylinder 121T is arranged in the upper cylinder inner wall 123T, and as shown in FIG. 3, a refrigerant is applied between the upper cylinder inner wall 123T and the upper piston 125T. An upper compression chamber 133T is formed which sucks, compresses, and discharges. Similarly, the lower cylinder 121S is formed with the lower cylinder inner wall 123S along a concentric circle with the rotating shaft 15 of the motor 11. A lower piston 125S having an outer diameter smaller than the inner diameter of the lower cylinder 121S is arranged in the lower cylinder inner wall 123S, and as shown in FIG. 3, a refrigerant is introduced between the lower cylinder inner wall 123S and the lower piston 125S. A lower compression chamber 133S that sucks, compresses, and discharges is formed.

As shown in FIG. 3, the upper cylinder 121T has an upper protruding portion 122T protruding in the radial direction of the rotating shaft 15 from the circular outer peripheral portion. The upper protruding portion 122T is provided with an upper vane groove 128T extending outward radially from the upper cylinder chamber 130T. The upper vane 127T is slidably arranged in the upper vane groove 128T. The lower cylinder 121S has a downward protruding portion 122S protruding in the radial direction of the rotating shaft 15 from the circular outer peripheral portion. The lower side protrusion 122S is provided with a lower vane groove 128S extending outward radially from the lower cylinder chamber 130S. The lower vane 127S is slidably arranged in the lower vane groove 128S.

The upper protrusion 122T and the lower protrusion 122S are formed over a predetermined protrusion range along the circumferential direction of the rotation shaft 15. The upper protruding portion 122T and the lower protruding portion 122S are used as chuck holding portions for fixing to the processing jig at the time of processing the upper cylinder 121T and the lower cylinder 121S.

The upper cylinder 121T is provided with an upper spring hole 124T that communicates with the upper vane groove 128T from the outer surface of the upper protruding portion 122T at a depth that does not penetrate the upper cylinder chamber 130T. In the upper spring hole 124T, an upper spring 126T that presses the back surface of the upper vane 127T is arranged. The lower cylinder 121S is provided with a lower spring hole 124S that communicates with the lower vane groove 128S from the outer surface of the lower protruding portion 122S at a depth that does not penetrate the lower cylinder chamber 130S. In the lower spring hole 124S, a lower spring 126S that presses the back surface of the lower vane 127S is arranged.

Further, the compressed refrigerant in the compressor housing 10 is introduced into the lower cylinder 121S by communicating the radial outside of the lower vane groove 128S and the inside of the compressor housing 10, and the pressure of the refrigerant is introduced into the lower vane 127S. A lower pressure introduction path 129S for applying back pressure is formed. Further, the compressed refrigerant in the compressor housing 10 is introduced into the upper cylinder 121T by communicating the radial outside of the upper vane groove 128T and the inside of the compressor housing 10 at an opening, and introduces the compressed refrigerant into the upper vane 127T. An upper pressure introduction path 129T that applies back pressure by the pressure of the refrigerant is formed.

As shown in FIG. 2, the upper protrusion 122T of the upper cylinder 121T is provided with an upper suction hole 135T that fits with the upper suction pipe 105. The lower protrusion 122S of the lower cylinder 121S is provided with a lower suction hole 135S that fits with the lower suction pipe 104.

As shown in FIG. 3, the upper cylinder chamber 130T is closed at the upper and lower ends by an upper end plate 160T and an intermediate partition plate 140, respectively. The lower cylinder chamber 130S is closed at the upper and lower ends by an intermediate partition plate 140 and a lower end plate 160S, respectively.

As shown in FIG. 3, the upper vane 127T is pressed by the urging force of the upper spring 126T and protrudes from the upper vane groove 128T into the upper cylinder 121T, and the tip portion 138T of the upper vane 127T is attached to the outer peripheral surface 139T of the upper piston 125T. Contact. As a result, the upper cylinder chamber 130T is divided into an upper suction chamber 131T communicating with the upper suction hole 135T and an upper compression chamber 133T communicating with the upper discharge hole 190T provided on the upper end plate 160T. Similarly, the lower vane 127S is pressed by the urging force of the lower spring 126S and protrudes from the lower vane groove 128S into the lower cylinder 121S, and the tip portion 138S of the lower vane 127S abuts on the outer peripheral surface 139S of the lower piston 125S. As a result, the lower cylinder chamber 130S is divided into a lower suction chamber 131S communicating with the lower suction hole 135S and a lower compression chamber 133S communicating with the lower discharge hole 190S provided in the lower end plate 160S.

Further, the upper discharge hole 190T is provided close to the upper vane groove 128T, and the lower discharge hole 190S is provided close to the lower vane groove 128S. The refrigerant compressed in the upper compression chamber 133T and the lower compression chamber 133S is discharged from the upper compression chamber 133T and the lower compression chamber 133S through the upper discharge hole 190T and the lower discharge hole 190S.

As shown in FIG. 2, the upper end plate 160T is provided with an upper discharge hole 190T that penetrates the upper end plate 160T and communicates with the upper compression chamber 133T of the upper cylinder 121T. An upper valve seat (not shown) is formed around the upper discharge hole 190T at the opening edge on the outlet side of the upper discharge hole 190T so as to project toward the upper discharge valve 200T, which will be described later. The upper end plate 160T is formed with an upper discharge valve accommodating recess 164T extending in a groove shape from the position of the upper discharge hole 190T toward the outer periphery of the upper end plate 160T.

In the upper discharge valve accommodating recess 164T, a lead valve type upper discharge valve 200T whose base end portion is fixed in the upper discharge valve accommodating recess 164T by an upper rivet 202T and whose tip portion opens and closes the upper discharge hole 190T, and a base end portion. Is overlapped with the upper discharge valve 200T and fixed in the upper discharge valve accommodating recess 164T by the upper rivet 202T, and the tip portion is curved (warped) in the direction in which the upper discharge valve 200T opens to increase the opening degree of the upper discharge valve 200T. The entire upper discharge valve retainer 201T to be regulated is accommodated.

The lower end plate 160S is provided with a lower discharge hole 190S that penetrates the lower end plate 160S and communicates with the lower compression chamber 133S of the lower cylinder 121S. An annular lower valve seat surrounding the lower discharge hole 190S is formed at the opening edge on the outlet side of the lower discharge hole 190S so as to project toward the lower discharge valve 200S, which will be described later. The lower end plate 160S is formed with a lower discharge valve accommodating recess (not shown) extending in a groove shape from the position of the lower discharge hole 190S toward the outer periphery of the lower end plate 160S.

The lower discharge valve accommodating recess accommodates a reed valve type lower discharge valve 200S that opens and closes the lower discharge hole 190S, and the entire lower discharge valve retainer 201S that regulates the opening degree of the lower discharge valve 200S. The lower discharge valve 200S is formed of a metal material in a leaf spring shape. The base end of the lower discharge valve 200S is fixed in the lower discharge valve accommodating recess by the lower rivet 202S, and the tip portion opens and closes the lower discharge hole 190S by elastic deformation. The lower discharge valve retainer 201S has a base end portion overlapped with the lower discharge valve 200S and fixed in the lower discharge valve accommodating recess by the lower rivet 202S, and the tip end portion is curved in the direction in which the lower discharge valve 200S opens ( The opening of the lower discharge valve 200S is regulated by the warped tip portion in contact with the lower discharge valve 200S.

An upper end plate cover chamber 180T is formed between the upper end plate 160T fixed in close contact with each other and the upper end plate cover 170T having a bulging portion. A lower end plate cover chamber 180S (see FIG. 1) is formed between the lower end plate 160S which is closely fixed to each other and the flat end plate cover 170S. A refrigerant passage hole 136 is provided that penetrates the lower end plate 160S, the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T and communicates the lower end plate cover chamber 180S and the upper end plate cover chamber 180T.

The flow of the refrigerant due to the rotation of the rotating shaft 15 will be described below. In the upper cylinder chamber 130T, the upper piston 125T fitted to the upper eccentric portion 152T of the rotating shaft 15 is placed on the outer peripheral surface of the upper cylinder chamber 130T (inner peripheral surface of the upper cylinder 121T) by the rotation of the rotating shaft 15. By revolving along the circumference, the upper suction chamber 131T sucks the refrigerant from the upper suction pipe 105 while expanding the volume, the upper compression chamber 133T compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is discharged upward. When the pressure becomes higher than the pressure of the upper end plate cover chamber 180T on the outer side of the valve 200T, the upper discharge valve 200T opens and the refrigerant is discharged from the upper compression chamber 133T to the upper end plate cover chamber 180T. The refrigerant discharged into the upper end plate cover chamber 180T is discharged into the compressor housing 10 from the upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T.

Further, in the lower cylinder chamber 130S, the lower piston 125S fitted to the lower eccentric portion 152S of the rotating shaft 15 due to the rotation of the rotating shaft 15 is attached to the outer peripheral surface of the lower cylinder chamber 130S (the inner peripheral surface of the lower cylinder 121S). ), The lower suction chamber 131S sucks the refrigerant from the lower suction pipe 104 while expanding the volume, and the lower compression chamber 133S compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is increased. When the pressure becomes higher than the pressure of the lower end plate cover chamber 180S on the outer side of the lower discharge valve 200S, the lower discharge valve 200S opens and the refrigerant is discharged from the lower compression chamber 133S to the lower end plate cover chamber 180S. The refrigerant discharged into the lower end plate cover chamber 180S is discharged into the compressor housing 10 from the upper end plate cover discharge hole 172T provided in the upper end plate cover 170T through the refrigerant passage hole 136 and the upper end plate cover chamber 180T. ..

The refrigerant discharged into the compressor housing 10 is a notch (not shown) provided on the outer periphery of the stator 111 that communicates vertically, a gap in the winding portion of the stator 111 (not shown), or the stator 111. It is guided above the motor 11 through a gap 115 (see FIG. 1) between the rotor 112 and the rotor 112, and is discharged from a discharge pipe 107 as a discharge portion arranged at the upper part of the compressor housing 10.

(Characteristic configuration of rotary compressor)
Next, the characteristic configuration of the rotary compressor 1 of the embodiment will be described. FIG. 4 shows a gap formed between the tip portion 138T of the upper vane 127T and the outer peripheral surface 139T of the upper piston 125T, the tip portion 138S of the lower vane 127S and the outer peripheral surface 139S of the lower piston 125S in the rotary compressor 1 of the embodiment. It is a cross-sectional view for demonstrating the gap which occurs between.

In the rotary compressor 1 of the present embodiment, as the refrigerant, an HFO1123 refrigerant having a property of causing a disproportionation reaction when energy is applied under constant temperature and pressure conditions, or a mixed refrigerant containing the HFO1123 refrigerant is used. Has been done. Therefore, in the rotary compressor 1 of the present embodiment, liquid compression of the refrigerant occurs in the upper compression chamber 133T (hereinafter, the same applies to the lower compression chamber 133S, and the description of the lower compression chamber 133S will be omitted). In order to avoid high pressure in the upper compression chamber 133T, when the pressure in the upper compression chamber 133T reaches a predetermined pressure, the liquid is actively released from the upper compression chamber 133T to release the liquid. The feature is that it suppresses the disproportionation reaction of the refrigerant when compression occurs.

When the rotary compressor is driven at a low pressure ratio, the pressure for pressing the upper vane (lower vane) against the upper piston (lower piston) becomes lower, and when driven at a higher rotation speed, it acts on the upper vane (lower vane). Since the centrifugal force is increased, the tip of the upper vane (lower vane) and the outer peripheral surface of the upper piston (lower piston) located at the top dead center may be separated from each other. The upper spring and lower spring may be damaged due to the large displacement of the upper spring when the upper vane retracts with respect to the upper piston and the displacement of the lower spring when the lower vane retracts with respect to the lower piston. Will be higher. Therefore, in general, in a rotary compressor, it is preferable to make the gap between the tip of the upper vane (lower vane) and the outer peripheral surface of the upper piston (lower piston) as small as possible.

On the other hand, the rotary compressor 1 of this embodiment is premised on using a refrigerant that may cause a disproportionation reaction due to liquid compression, and has an upper vane 127T tip portion 138T and an upper piston 125T. A gap is intentionally opened between the outer peripheral surface 139T and the outer peripheral surface 139S of the lower vane 127S and the tip portion 138S of the lower piston 125S.

Specifically, as shown in FIG. 4, the upper vane 127T has a second pressure P2 in the upper compression chamber 133T rather than a first pressure P1 in the upper pressure introduction path 129T on one end side of the upper vane groove 128T. When the pressure is higher than the predetermined pressure, the upper vane groove so as to open a predetermined gap D for passing the refrigerant between the tip portion 138T (sliding surface) of the upper vane 127T and the outer peripheral surface 139T of the upper piston 125T. It is provided in 128T. Similarly, when the second pressure P2 in the lower compression chamber 133S is larger than the first pressure P1 in the lower pressure introduction path 129S on one end side of the lower vane groove 128S, the lower vane 127S is larger than a predetermined pressure. The lower vane groove 128S is provided so as to open a predetermined gap D for passing the refrigerant between the tip portion 138S of the lower vane 127S and the outer peripheral surface 139S of the lower piston 125S. The first pressure P1 and the second pressure P2 are equal in each of the upper cylinder 121T and the lower cylinder 121S.

That is, when the second pressure P2 in the upper compression chamber 133T becomes equal to or higher than a predetermined pressure, the refrigerant (liquid refrigerant and gas refrigerant) in the upper compression chamber 133T is passed through the gap D between the upper vane 127T and the upper piston 125T. For example, the upper vane 127T retracts into the upper vane groove 128T in order to sufficiently escape to the upper suction chamber 131T and sufficiently escape into the compressor housing 10 through the upper vane groove 128T and the upper pressure introduction portion 129T. A vane 127T is provided in the upper vane groove 128T. Similarly, when the second pressure P2 in the lower compression chamber 133S becomes equal to or higher than a predetermined pressure, the refrigerant (liquid refrigerant and gas refrigerant) in the lower compression chamber 133S passes through the gap D between the lower vane 127S and the lower piston 125S. Is sufficiently released into the compressor housing 10 through the lower vane groove 128S and the lower pressure introduction portion 129S, for example, so that the lower vane 127S retreats into the lower vane groove 128S. The lower vane 127S is provided in the lower vane groove 128S. In this way, when the pressure inside the upper compression chamber 133T exceeds a predetermined pressure, the upper vane 127T recedes into the upper vane groove 128T, and between the tip portion 138T of the upper vane 127T and the outer peripheral surface 139T of the upper piston 125T. The urging force and mechanical strength of the upper spring 126T, the length of the upper vane 127T with respect to the advancing / retreating direction of the upper vane 127T, and the length of the upper vane groove 128T are set so as to open a gap D having a predetermined dimension d. (The same applies to the lower vane 127S, etc.).

The thickness of the upper vane 127T with respect to the circumferential direction of the upper cylinder 121T and the thickness of the lower vane 127S with respect to the circumferential direction of the lower cylinder 121S are set to, for example, 3.2 mm or more. The movable range of the upper vane 127T in the upper vane groove 128T accompanying the revolution of the upper piston 125T with respect to the advancing / retreating direction, and the movable range of the lower vane 127S in the lower vane groove 128S accompanying the revolution of the lower piston 125S with respect to the advancing / retreating direction are, for example. It is set to about 11 mm. This movable range includes the dimensional tolerances (for example, about 0.5 mm) of the lengths of the upper vane 127T and the lower vane 127S.

In the rotary compressor 1 of the embodiment, the first pressure P1 is about 3 MPa and the second pressure P2 is about 5 MPa, and the upper vane 127T and the lower vane 127S are the steps of compressing the refrigerant by revolving the upper piston 125T and the lower piston 125S. When the second pressure P2 becomes 1.5 times or more the first pressure P1, between the tip portion 138T of the upper piston 127T and the outer peripheral surface 139T of the upper piston 125T, and the tip portion of the lower piston 127S. It is configured to open a gap D having a predetermined dimension d between the 138S and the outer peripheral surface 139S of the upper and lower pistons 125S. Further, the upper vane 127T and the lower vane 127S are configured to open a gap D having a predetermined dimension d when, for example, the second pressure P2 becomes 5 MPa or more. Since the upper pressure introduction path 129T and the lower pressure introduction path 129S are communicated with the inside of the compressor housing 10, the first pressure P1 in the upper pressure introduction path 129T and the lower pressure introduction path 129S is the compressor housing. Equal to the pressure in body 10.

Further, the gap D having the predetermined dimension d described above is 0.5 mm or more and 1.0 mm in the advancing / retreating direction of the upper vane 127T (diameter direction of the upper cylinder 121T) with the upper piston 125T located at the top dead center. It is set as follows (the same applies to the lower vane 127S). When the dimension d of the gap D exceeds 1.0 mm, the displacement amount of the upper spring 126T when the upper vane 127T retracts with respect to the upper piston 125T, and when the lower vane 127S retracts with respect to the lower piston 125S. The amount of displacement of the lower spring 126S becomes large, and the risk of damage to the upper spring 126T and the lower spring 126S increases, which is not preferable. On the other hand, when the dimension d of the gap D is less than 0.5 mm, it is difficult to properly release the high-pressure refrigerant from the upper compression chamber 133T and the lower compression chamber 133S, which is not preferable.

Even when the upper piston 125T is located at the top dead center, when the second pressure P2 in the upper compression chamber 133T reaches a predetermined pressure or more due to the liquid compression occurring in the upper compression chamber 133T. In addition, the upper vane 127T recedes from the upper piston 125T, and a gap D having a predetermined dimension d opens. The refrigerant in the upper compression chamber 133T is discharged from the gap D through the upper suction chamber 131T, the upper vane groove 128T, and the like into the compression housing 10. Therefore, the second pressure P2 in the upper compression chamber 133T is appropriately lowered. Therefore, it is possible to prevent the refrigerant from undergoing a disproportionation reaction when liquid compression occurs in the upper compression chamber 133T (the same applies to the lower compression chamber 133S).

As described above, the rotary compressor 1 of the embodiment uses the HFO1123 refrigerant or the mixed refrigerant containing the HFO1123 refrigerant as the refrigerant, and the first pressure P1 in the upper pressure introduction path 129T on one end side of the upper vane groove 128T. When the second pressure P2 in the upper compression chamber 133T is larger than the predetermined pressure, a gap D having a predetermined dimension d is formed between the tip portion 138T of the upper vane 127T and the outer peripheral surface 139T of the upper piston 125T. open. As a result, when liquid compression occurs in the upper compression chamber 133T, the refrigerant can be released from the upper compression chamber 133T through the gap D between the upper vane 127T and the upper piston 125T. Therefore, since it is possible to prevent the pressure inside the upper compression chamber 133T from becoming high due to liquid compression, it is possible to suppress the occurrence of a disproportionation reaction in the refrigerant (the same applies to the lower vane 127S).

Further, the upper vane 127T in the rotary compressor 1 of the embodiment opens a gap D having a predetermined dimension d when the second pressure P2 becomes 1.5 times or more the first pressure P1. As a result, when liquid compression occurs in the upper compression chamber 133T, the refrigerant can be properly released from the upper compression chamber 133T, the pressure in the upper compression chamber 133T is effectively reduced, and the refrigerant is disproportionated to the refrigerant. It is possible to suppress the reaction from occurring (the same applies to the lower vane 127S).

Further, the upper vane 127T in the rotary compressor 1 of the embodiment opens a gap D having a predetermined dimension d when the second pressure P2 becomes 5 MPa or more. As a result, when liquid compression occurs in the upper compression chamber 133T, the refrigerant can be properly released from the upper compression chamber 133T, the pressure in the upper compression chamber 133T is effectively reduced, and the refrigerant is disproportionated to the refrigerant. It is possible to suppress the reaction from occurring (the same applies to the lower vane 127S).

Further, in the rotary compressor 1 of the embodiment, the gap D having a predetermined dimension d is 0.5 mm or more and 1.0 mm or less in the advancing / retreating direction of the upper vane 127T. As a result, the upper spring 126T can be suppressed from being damaged, and the high-pressure refrigerant can be appropriately released from the upper compression chamber 133T (the same applies to the lower vane 127S).

Further, although the above-described embodiment has been applied to the 2-cylinder type rotary compressor 1, it may be applied to the 1-cylinder type rotary compressor, and the 1-cylinder type has the same effect as the 2-cylinder type. Obtainable.

1 Rotary compressor 10 Compressor housing 11 Motor 12 Compressor 15 Rotating shaft 25 Accumulator 105 Upper suction pipe (suction)
104 Lower suction pipe (suction part)
107 Discharge pipe (discharge part)
111 Stator 112 Rotor 121T Upper cylinder 121S Lower cylinder 124T Upper spring hole 124S Lower spring hole 125T Upper piston 125S Lower piston 126T Upper spring 126S Lower spring 127T Upper vane 127S Lower vane 128T Upper vane groove 128S Lower vane groove 129T Upper pressure introduction path 129S Lower pressure introduction path 130T Upper cylinder chamber 130S Lower cylinder chamber 131T Upper suction chamber 131S Lower suction chamber 133T Upper compression chamber 133S Lower compression chamber 138T, 138S Tip part 139T, 139S Outer peripheral surface 152T Upper eccentric part 152S Lower eccentric part 160T Upper end Plate 160S Lower end plate 190T Upper discharge hole 190S Lower discharge hole d Dimension D Gap P1 First pressure P2 Second pressure

Claims (4)

A vertically placed cylindrical compressor housing with a refrigerant discharge part provided at the upper part and a refrigerant suction part provided at the lower part, and a refrigerant arranged at the lower part of the compressor housing and sucked from the suction part. It has a compression unit that compresses and discharges from the discharge unit, and a motor that is arranged in the upper part of the compressor housing and drives the compression unit.
The compression portion includes an annular cylinder, an upper end plate that closes the upper side of the cylinder, a lower end plate that closes the lower side of the cylinder, a rotating shaft having an eccentric portion and being rotated by the motor, and the above. A piston that is fitted into an eccentric portion and revolves along the inner peripheral surface of the cylinder to form a cylinder chamber in the cylinder, and a vane groove provided in the cylinder that protrudes into the cylinder chamber and has a tip portion on the piston. A vane that divides the cylinder chamber into a suction chamber and a compression chamber by abutting, a spring that is arranged on one end side of the vane groove and urges the vane to the cylinder chamber, and one end side of the vane groove and the compression. A pressure introduction path that communicates with the inside of the machine housing, and a discharge hole that discharges the refrigerant compressed in the compression chamber from the compression chamber.
In a rotary compressor with
The refrigerant is an HFO1123 refrigerant or a mixed refrigerant containing the HFO1123 refrigerant.
When the second pressure in the compression chamber is larger than a predetermined pressure than the first pressure in the pressure introduction path on one end side of the vane groove, the vane of the vane and the piston A rotary compressor characterized in that a predetermined gap is opened between the outer peripheral surface and the outer peripheral surface. The vane opens the predetermined gap when the second pressure becomes 1.5 times or more the first pressure.
The rotary compressor according to claim 1. The vane opens the predetermined gap when the second pressure becomes 5 MPa or more.
The rotary compressor according to claim 1 or 2. The predetermined gap is 0.5 mm or more and 1.0 mm or less in the advancing / retreating direction of the vane.
The rotary compressor according to any one of claims 1 to 3.

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