WO2014103974A1

WO2014103974A1 - Gas compressor

Info

Publication number: WO2014103974A1
Application number: PCT/JP2013/084390
Authority: WO
Inventors: 津田　昌宏; 俊勝宮地; 貴之飯盛
Original assignee: カルソニックカンセイ株式会社
Priority date: 2012-12-26
Filing date: 2013-12-23
Publication date: 2014-07-03

Abstract

Provided is a gas compressor that supplies high-pressure back pressure to the vanes in the final stage of the compression step. A compressor main body (60) is provided in a housing (10) and has: a rotor (50) in which vane grooves (59) are formed; a cylinder (40) having an inner circumferential surface (41) the contour shape of which encloses the outer peripheral surface (52) of the rotor (50) from the outside; and five plate-like vanes (58), which are inserted into the vane grooves (59), and are provided so as to be capable of receiving back pressure from refrigerant oil (R) supplied from drain grooves (21, 31) to the vane grooves (59), and to protrude toward the inner circumferential surface (41) of the cylinder (40). A compression chamber (43), which compresses indrawn refrigerant gas (G) once per rotation of the rotor (50), is formed in the cylinder main body. The drain grooves (21, 31) communicate with the vane grooves (59) in a prescribed rotational angle range (α) of the rotor (50), and the vane grooves (59) form a closed space in another rotational angle range (β) that excludes the rotational angle range (α) wherein the drain grooves (21, 31) communicate with the vane grooves (59).

Description

Gas compressor

The present invention relates to a gas compressor, and more particularly, to an improvement of a vane rotary type gas compressor.

In the air conditioning system, a gas compressor for compressing a gas such as a refrigerant gas and circulating the gas in the air conditioning system (air conditioning system) is used.

This gas compressor discharges the high-pressure gas compressed by the compressor body housed inside the housing to the outside.

Conventionally, a vane rotary type gas compressor is known as such a gas compressor (for example, refer to Patent Document 1).

The vane rotary type gas compressor has a substantially cylindrical rotor whose compressor body rotates integrally with a rotation shaft, and a cylinder having a contour-shaped inner peripheral surface surrounding the rotor from the outside of the peripheral surface. And a plurality of plate-like vanes that are accommodated in vane grooves formed in the rotor and protrude outwardly from the circumferential surface of the rotor, and the outer circumferential surface of the rotor and the inner circumferential surface of the cylinder, etc. A cylinder chamber, which is a space in which gas is sucked, compressed, and discharged, is formed.

This cylinder chamber is partitioned into a plurality of compression chambers, with the protruding tip of each vane protruding outward from the outer peripheral surface of the rotor in contact with the inner peripheral surface of the cylinder.

The gas compressed to a high pressure in each compression chamber is discharged from the compressor body, and after the oil (such as refrigeration oil) mixed in the discharged gas is separated, it is discharged to the outside.

On the other hand, the oil separated from the gas is stored at the bottom of the discharge chamber, receives the pressure of the discharged high-pressure gas, is supplied to the vane groove through the oil passage, and functions as a back pressure that causes the vane to protrude.

JP 2009-228520 A

By the way, for example, in a gas compressor formed with a long compression stroke, the pressure in the compression chamber before and after the vane may be increased, and the pressure acting on the vane becomes very high. As a result, a very high pressure is required.

However, since what is described in Patent Document 1 is a structure that uses an oil component having a pressure corresponding to the pressure of the discharged gas as a back pressure, the back pressure is the pressure (high pressure) of the discharged gas. It does not exceed, and a very high pressure exceeding the pressure of the discharged gas cannot be supplied as a back pressure.

The present invention has been made in view of the above circumstances, and is a gas compressor capable of supplying a high pressure exceeding the pressure of the compressed gas discharged from the compression chamber as the back pressure of the vane in the final stage of the compression stroke or in the discharge stroke. The purpose is to provide.

The gas compressor according to the present invention cuts off the communication between the rotor vane groove (back pressure space) and the oil passage after the middle stage of the compression stroke, so that the back pressure space is filled with oil (completely oil content). Not only in a state of being filled with only gas, but also in a state where a slight amount of gas is mixed), and as the compression process proceeds, the back pressure space is brought into a liquid compression state by a vane. Thus, a high pressure exceeding the pressure of the compressed gas is obtained as the back pressure of the vane in the final stage of the compression stroke or in the discharge stroke.

That is, the gas compressor according to the present invention includes a substantially cylindrical rotor that rotates about an axis, and an inner peripheral surface having a contour shape that surrounds the rotor from the outer peripheral surface with a clearance from the outer peripheral surface of the rotor. And a cylinder that is inserted into a vane groove formed in the rotor, and is provided so as to protrude outwardly from the outer peripheral surface of the rotor by receiving a back pressure from refrigeration oil supplied to the vane groove from a predetermined oil passage. A compressor body having a plurality of plate-like vanes and having a compression chamber formed therein that compresses gas at a rate of once during one rotation of the rotor. Is formed so as to block communication with the vane groove within a predetermined rotation angle range of the rotor.

According to the gas compressor of the present invention, a high pressure exceeding the pressure of the compressed gas discharged from the compression chamber can be supplied to the vane as a back pressure at the end of the compression stroke.

The cross-sectional view of the vane rotary compressor as a gas compressor concerning each embodiment of the present invention. FIG. 2 is a cross-sectional view of the compressor body of the vane rotary compressor illustrated in FIG. 1 taken along line AA. The figure which shows the range of the rotation angle in which the Saray groove was formed in the inner surface of a rear side block in Embodiment 1 of this invention, and the range of the rotation angle made into the space where the vane groove was closed. The figure which shows the Sarai groove in the inner surface of a rear side block in Embodiment 2 of this invention, the range of the rotation angle in which the high pressure oil path was formed, and the range of the rotation angle made into the space where the vane groove was closed. The figure which showed the range of the fine recessed part formed in the cylinder internal peripheral surface in Embodiment 3 of this invention. It is an expanded sectional view of the fine recessed part formed in the cylinder internal peripheral surface. The figure which shows the change state of the back pressure which acted on the pressure in a compression chamber, and a vane at the time of the suction process of gas, the compression process, and the discharge process of Embodiment 4 of this invention. In Embodiment 4 of this invention, the figure which shows the state which pressure-reduced back pressure raised by predetermined amount. The figure which shows the inner surface of the rear side block in Embodiment 4 of this invention. The figure which shows the outer surface side of the rear side block in Embodiment 4 of this invention. FIG. 9B is a sectional view taken along line BB in FIG. 9A. The figure which shows the state in which the hole formed in the outer surface of a rear side block is connecting with the vane groove | channel in Embodiment 4 of this invention. The figure which shows the inner surface side of the rear side block in Embodiment 5 of this invention. The figure which showed the positional relationship of the hole by the side of a rear side block, the communicating groove | channel, and a vane groove | channel in Embodiment 5 of this invention. The figure which shows the outer surface side of the rear side block in Embodiment 5 of this invention. FIG. 13C is a cross-sectional view taken along the line CC of FIG. 13A. The figure which shows the state which the hole formed in the outer surface of the rear side block in Embodiment 5 of this invention is connected to the vane groove through the communication groove. In Embodiment 5 of this invention, the figure which shows the state which pressure-reduced back pressure raised by predetermined amount. The figure which shows the inner surface side of the rear side block in Embodiment 6 of this invention. The figure which shows the outer surface side of the rear side block in Embodiment 6 of this invention. FIG. 17D is a sectional view taken along line DD of FIG. 17A.

Hereinafter, specific embodiments of the gas compressor according to the present invention will be described in detail with reference to the drawings.

<Embodiment 1>
A vane rotary compressor (hereinafter simply referred to as a “compressor”) 1 which is an embodiment of a gas compressor according to the present invention includes an evaporator, a gas compressor, a condenser, and an expansion valve (all of which are installed in an automobile or the like). It is used as a gas compressor in an air conditioning system having (not shown). This air conditioning system constitutes a refrigeration cycle by circulating a refrigerant gas G (gas).

As shown in FIG. 1, the compressor 1 mainly includes a motor 90, a compressor body 60, and an oil separator 70 housed in a housing 10 including a body case 11 and a front cover 12. It is a configuration.

The main body case 11 has a substantially cylindrical shape, and is formed such that one end of the cylindrical shape is closed, and the other end is opened.

The front cover 12 is formed in a lid shape so as to close the opening while being in contact with the opening-side end portion of the main body case 11. In this state, the front cover 12 is fastened to the main body case 11 by a fastening member. And a housing 10 having a space inside is formed.

The front cover 12 is formed with a suction port 12a through which the low-pressure refrigerant gas G is introduced into the housing 10 from an evaporator (not shown) of the air conditioning system through the inside and the outside of the housing 10.

On the other hand, the main body case 11 is formed with a discharge port 11a through which the high pressure refrigerant gas G is discharged from the inside of the housing 10 to the condenser (not shown) of the air conditioning system through the inside and the outside of the housing 10. Yes.

The motor 90 provided inside the main body case 11 constitutes a multiphase brushless DC motor including a permanent magnet rotor 90a and an electromagnet stator 90b.

The stator 90b is fitted and fixed to the inner peripheral surface of the main body case 11, and the rotating shaft 51 is fixed to the rotating rotor 90a.

In the motor 90, the rotor 90a is rotationally driven by exciting the electromagnet of the stator 90b with the electric power supplied via the power connector 90c attached to the front cover 12. As a result, the rotary shaft 51 is driven to rotate about its axis.

It should be noted that a configuration including an inverter circuit 90d or the like can be employed between the power connector 90c and the stator 90b.

As described above, the compressor 1 of the present embodiment is an electric type using the motor 90, but the gas compressor according to the present invention is not limited to the electric type, and is a mechanical type. May be.

For example, if the compressor 1 of this embodiment is a mechanical type, instead of providing the motor 90, the rotary shaft 51 is extended from the front cover 12 to the outside and protrudes from the front cover 12. What is necessary is just to set it as the structure provided in the front-end | tip part of the rotating shaft 51 with the pulley, gearwheel, etc. which receive motive power transmission from the engine etc. of a vehicle.

The compressor main body 60 accommodated in the housing 10 together with the motor 90 is arranged side by side with the motor 90 along the direction in which the rotating shaft 51 extends, and is fixed to the main body case 11 by a fastening member 15 such as a bolt. Has been.

The compressor main body 60 accommodated in the housing 10 includes a rotating shaft 51 that is rotatable about an axis, a substantially cylindrical rotor 50 that rotates integrally with the rotating shaft 51, and a rotating shaft 51 that rotates integrally with the rotating shaft 51, as shown in FIG. The rotor 50 is inserted into a cylinder 40 having a contoured inner peripheral surface 41 that surrounds the outer peripheral surface 52 from the outside, and a vane groove 59 formed in the rotor 50, respectively. The five plate-like vanes 58 provided to protrude from the outer peripheral surface 52 of the rotor 50 toward the inner peripheral surface 41 of the cylinder 40 under the back pressure by the supplied refrigerating machine oil R, the rotor 50 and the cylinder 40. The two side blocks (front side block 20 and rear side block 30) are provided so as to be in contact with the both end surfaces of and cover the both end surfaces.

Here, the rotating shaft 51 is rotatably supported by bearings 12b formed on the front cover 12 and

bearings

27 and 37 formed on the side blocks 20 and 30 of the compressor main body 60, respectively.

Further, the compressor main body 60 partitions the space inside the housing 10 into a left space and a right space sandwiching the compressor main body 60.

Of the two spaces partitioned inside the housing 10, the space on the left side with respect to the compressor body 60 is supplied with the low-pressure refrigerant gas G from the evaporator through the suction port 12a, and the low-pressure refrigerant gas G is compressed. The suction chamber 13 is in a low-pressure atmosphere that passes before being sucked into the machine main body 60, and the motor 90 is disposed in the suction chamber 13.

On the other hand, the space on the right side of the compressor body 60 passes before the high-pressure refrigerant gas G discharged from the compressor body 60 via the oil separator 70 is discharged from the discharge port 11a to the condenser. The discharge chamber 14 is a high-pressure atmosphere.

As shown in FIG. 2, the compressor main body 60 has a substantially C-shaped single body surrounded by an inner peripheral surface 41 of the cylinder 40, an outer peripheral surface 52 of the rotor 50, and both side blocks 20 and 30. A cylinder chamber 42 is formed.

Specifically, the cylinder 40 is arranged such that the inner circumferential surface 41 of the cylinder 40 and the outer circumferential surface 52 of the rotor 50 are close to each other in a range of one round (an angle of 360 degrees) around the axis of the rotating shaft 51. The contour shape of the inner peripheral surface 41 is set, and thereby the cylinder chamber 42 forms a single space.

Of the contour shape of the inner peripheral surface 41 of the cylinder 40, the portion where the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are farthest away (the distance from the outer peripheral surface 52 of the rotor 50 is maximum). The remote portion 49 formed as a portion where the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are closest to each other (the distance from the outer peripheral surface 52 of the rotor 50 is minimized). 48 is formed at a position biased upstream in the rotational direction W of the rotor 50 (clockwise direction in FIG. 2).

That is, from the remote portion 49, the rotation angle is greater than 180 degrees along the rotation direction W of the rotor 50 (in this embodiment, the angle is 270 degrees or more (less than 360 degrees), but the degree of the bias is 58. The proximity portion 48 is formed at a position that can be changed as appropriate according to the number of sheets.

The contour shape of the inner peripheral surface 41 of the cylinder 40 is such that the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 41 of the cylinder 40 extend from the remote portion 49 to the proximity portion 48 along the rotation direction W of the rotating shaft 51 and the rotor 50. The shape is set such that the distance between and gradually decreases.

The vane 58 is accommodated in a vane groove 59 formed in the rotor 50, and protrudes outward from the outer peripheral surface 52 of the rotor 50 by back pressure due to the refrigerating machine oil R supplied to the vane groove 59 from an oil passage described later. To do.

The vane 58 partitions the single cylinder chamber 42 into a plurality of compression chambers 43, and one compression chamber 43 is provided by two vanes 58 that move back and forth along the rotation direction W of the rotating shaft 51 and the rotor 50. Is formed.

Therefore, in the present embodiment in which five vanes 58 are installed around the rotation shaft 51 at an equal angular interval of 72 degrees, five to six compression chambers 43 are formed.

In addition, in the compression chamber 43 in which the proximity portion 48 exists between the two

vanes

58 and 58, the proximity portion 48 and the one vane 58 constitute one closed space, so that the two vanes 58 are provided. , 58, the compression chamber 43 in which the proximity portion 48 exists is divided into two

compression chambers

43, 43 by the proximity portion 48, so that there are six compression chambers 43 even for five vanes. Is formed.

The volume inside the compression chamber 43 obtained by partitioning the cylinder chamber 42 by the vane 58 gradually decreases along the rotation direction W from the remote portion 49 to the proximity portion 48.

A portion of the cylinder chamber 42 on the most upstream side in the rotation direction W of the rotor 50 (the nearest portion on the downstream side with respect to the proximity portion 48 along the rotation direction W of the rotor 50) is formed in the front side block 20. , A suction hole 23 communicating with the suction chamber 13 (in FIG. 2, the front side block 20 is positioned on the front side of this figure, and therefore, the suction hole 23 formed in the front side block 20 is indicated by an imaginary line of a two-dot chain line. Is coming).

On the other hand, in the portion of the cylinder chamber 42 on the most downstream side in the rotation direction W of the rotor 50 (the portion closest to the upstream side with respect to the proximity portion 48 along the rotation direction W), the discharge portion 45 formed in the cylinder 40 The discharge hole 45b faces, and on the upstream side, the discharge hole 46b of the second discharge portion 46 formed in the cylinder 40 faces.

The contour shape of the inner peripheral surface 41 of the cylinder 40 is such that the refrigerant gas G is sucked into the compression chamber 43 from the suction chamber 13 through the suction hole 23 formed in the front side block 20, and the refrigerant gas G in the compression chamber 43 is drawn. It is set so that the refrigerant and the discharge of the refrigerant gas G from the compression chamber 43 to the discharge part 45 through the discharge hole 45 b are performed only for one cycle during one rotation of the rotor 50.

That is, the cross-sectional contour shape of the inner peripheral surface 41 of the cylinder 40 ranges from the proximity portion 48 substantially in contact with the outer peripheral surface 52 of the rotor 50 to the remote portion 49 set within an angle of 90 degrees along the rotation direction W of the rotor 50. In this range, the distance between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 increases rapidly, and the angle from the remote portion 49 to the proximity portion 48 along the rotational direction W of the rotor 50 In a wide range of 270 degrees or more, the distance between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 is formed so as to be gradually reduced.

Then, after the vane 58 located on the downstream side in the rotation direction W of the rotor 50 in the compression chamber 43 starts to pass through the suction hole 23 near the proximity portion 48, the vane 58 is located on the upstream side in the rotation direction W of the rotor 50. In the range until the vane 58 is completely passed through the suction hole 23, it is compressed through the suction hole 23 due to the negative pressure due to the volume of the compression chamber 43 increasing as the rotor 50 rotates in the rotation direction W. This is a stroke (intake stroke) in which the refrigerant gas G is sucked into the chamber 43.

When the rotation of the rotor 50 advances and the vane 58 on the upstream side of the compression chamber 43 finishes passing through the suction hole 23 toward the downstream in the rotation direction W of the rotor 50, the compression chamber 43 becomes a closed space, Due to the rotation in the rotation direction W from the remote portion 49 toward the proximity portion 48, the volume of the compression chamber 43 decreases, and a stroke (compression stroke) in which the refrigerant gas G confined in the compression chamber 43 is compressed.

At the end of the compression stroke, the pressure inside the compression chamber 43 reaches a predetermined discharge pressure. At that time, when the compression chamber 43 reaches the

discharge portions

45 and 46 formed in front of the proximity portion 48, the compression is performed. This is a stroke (discharge stroke) in which the refrigerant gas G inside the chamber 43 is discharged to the

discharge portions

45 and 46 through

discharge holes

45b and 46b described later.

Then, during one rotation of the rotor 50, each compression chamber 43 repeats the suction stroke, the compression stroke, and the discharge stroke in this order, so that the low-pressure refrigerant gas G sucked from the suction chamber 13 becomes high pressure and is discharged. The

parts

45 and 46 are discharged into the discharge chamber 14 via the oil separator 70.

The oil separator 70 separates the refrigerating machine oil R from the refrigerant gas G mixed with the refrigerating machine oil R.

That is, inside the compressor main body 60, the refrigeration oil R is enclosed in order to supply the back pressure of the vane 58. However, the refrigeration oil R may be a gap between the vane 58 and the vane groove 59, It begins to ooze from a gap between the rotor 50 and the side blocks 20 and 30. And the functions such as lubrication and cooling in the contact portion between the rotor 50 and both side blocks 20, 30 and the contact portion between the vane 58 and the cylinder 40 and both side blocks 20, 30 are also exhibited. A part of the refrigerating machine oil R is mixed with the refrigerant gas G inside the compression chamber 43.

When refrigerant gas G with a large amount of refrigerating machine oil R mixed is discharged to the condenser, the efficiency of the air conditioning system is lowered. Therefore, it is necessary to separate refrigerating machine oil R from refrigerant gas G and use centrifugal force. The refrigerating machine oil R is separated by the oil separator 70.

Each

discharge part

45 and 46 has space (henceforth "discharge chamber") 45a and 46a enclosed by the outer peripheral surface of the cylinder 40, the internal peripheral surface of the main body case 11, and the rear side block 30. FIG. The

discharge chambers

45a and 46a are provided with

discharge holes

45b and 46b through which the

discharge chambers

45a and 46a and the compression chamber 43 pass,

discharge valves

45c and 46c, and valve supports 45d and 46d.

In the

discharge valves

45c and 46c, the pressure of the refrigerant gas G in the compression chamber 43 is equal to or higher than the pressure in the

discharge chambers

45a and 46a (the pressure of the refrigerant gas discharged to the discharge chamber 14 side (hereinafter referred to as “discharge pressure Pd”). At this time, the pressure difference of the refrigerant gas G in the compression chamber 43 causes the pressure in the

discharge chambers

45a and 46a to be elastically deformed so as to warp toward the

discharge chambers

45a and 46a due to the differential pressure. When the pressure is lower than the discharge pressure Pd, the discharge holes 45b and 46b are closed by the elastic force of the

discharge valves

45c and 46c, and the valve supports 45d and 46d are excessively disposed on the

discharge chambers

45a and 46a side. Prevent warping.

In the present embodiment, of the two

discharge units

45 and 46, the discharge unit provided on the downstream side in the rotation direction W of the rotor 50, that is, the discharge unit 45 on the side close to the proximity unit 48 is set as the main discharge unit. (Hereafter, this discharge part 45 is called "main discharge part 45").

The main discharge portion 45 is a portion that always discharges the refrigerant gas G compressed in the compression chamber 43 because the pressure in the compression chamber 43 always reaches the discharge pressure Pd while the compression chamber 43 is facing. It is.

On the other hand, of the two

discharge parts

45 and 46, the discharge part provided on the upstream side in the rotation direction W, that is, the discharge part 46 far from the proximity part 48 is defined as a secondary discharge part (hereinafter, referred to as “secondary discharge part”). This discharge part 46 is referred to as “sub-discharge part 46”).

The sub-discharge section 46 is over-compressed in the compression chamber 43 (compressed to a pressure exceeding the discharge pressure Pd) when the discharge pressure Pd is reached before the compression chamber 43 faces the main discharge section 45. This is provided to prevent this. That is, as shown in FIG. 2, only when the pressure of the compression chamber 43 (43A) reaches the discharge pressure Pd during the period when the compression chamber 43 (43A) faces the sub-discharge portion 46, the compression chamber The refrigerant gas G inside 43 (43A) is discharged from the sub discharge part 46. In addition, when the pressure in the compression chamber 43 (43A) does not reach the discharge pressure Pd, the refrigerant gas G inside the compression chamber 43 (43A) is not discharged from the sub discharge portion 46 but faces the main discharge portion 45. It is discharged from the main discharge part 45 during a certain period.

The discharge chamber 45a of the main discharge unit 45 is an oil separator attached to the outer surface of the rear side block 30 through a discharge passage 38 formed so as to penetrate to the outer surface of the rear side block 30 (the surface facing the discharge chamber 14). 70.

Between the discharge chamber 45a of the main discharge portion 45 and the discharge chamber 46a of the sub discharge portion 46, a communication passage 39 is formed on the outer peripheral portion of the cylinder 40 through the

discharge chambers

45a and 46a. The discharge chamber 46 a communicates with the oil separator 70 attached to the outer surface of the rear side block 30 via the communication passage 39, the discharge chamber 45 a and the discharge passage 38.

As described above, the oil separator 70 separates the refrigerating machine oil R mixed with the refrigerant gas G from the refrigerant gas G. In the present embodiment, the oil separator 70 is discharged into the

discharge chambers

45a and 46a, Before discharging the high-temperature and high-pressure refrigerant gas G introduced through the discharge passage 38 into the discharge chamber 14, the refrigerating machine oil R is centrifuged from the refrigerant gas G by centrifugal force generated by swirling spirally. It has a structure.

The refrigerating machine oil R separated from the refrigerant gas G is accumulated at the bottom of the discharge chamber 14, and the high-pressure refrigerant gas G after the refrigerating machine oil R is separated is discharged into the discharge chamber 14 and then passes through the discharge port 11a. And discharged to the condenser.

The refrigerating machine oil R stored at the bottom of the discharge chamber 14 passes through an oil passage 34a formed in the rear side block 30 by a high-pressure atmosphere due to the high-pressure (same as the discharge pressure Pd) refrigerant gas G discharged into the discharge chamber 14. The rear side block 30 shown in FIG. 3 is supplied to the Sarai groove 31 which is a recess for supplying back pressure formed on the inner surface 35 facing the end surface 55b of the rotor 50.

Although FIG. 3 shows the rear side block 30, the front side block 20 can be expressed substantially symmetrically with respect to the rear side block 30.

The refrigerating machine oil R passes through the oil passages 34 a and 34 b formed in the rear side block 30, the oil passage 44 formed in the cylinder 40, and the oil passage 24 formed in the front side block 20. It is supplied to the Sarai groove 21, which is a recess for supplying back pressure, formed on the inner surface 25 facing the end surface 55 a of the rotor 50.

Here, each of the

Sarai grooves

21 and 31 is formed corresponding to a predetermined rotation angle range α (predetermined rotation angle range) along the rotation direction W of the rotor 50, and the oil passages 34 a and 34 b. , 44, 24 can be referred to as openings for expanding the outlets of the

inner surfaces

25, 35 to a wide range α of rotation angles.

As shown in FIGS. 2 and 3, the rotation angle range α in which the

Sarai grooves

21 and 31 are formed approaches the final stage of the compression stroke from when the compression chamber 43 is in the suction stroke (the compression chamber 43 is sub-discharged). Corresponds to the range up to the angular position).

The range α of the rotation angle is a position where the tip of the protruding side of the vane 58 positioned on the upstream side (rear side) in the rotation direction W of the compression chamber 43 is in contact with the proximity portion 48 of the cylinder 40 (rotation angle 0). Represents the rotation angle of the rotor 50 in the rotation direction W, and the rotation angle range α is set to, for example, 0 to 220 degrees.

However, the specific range of the rotation angle range α is not limited to the illustrated range, and the cross-sectional contour shape of the inner peripheral surface 41 of the cylinder 40, the number of vanes 58, and the set discharge pressure Pd. It is set as appropriate depending on the value.

In the compressor 1 of the present embodiment, the

oil passages

34a, 34b, 44, and 24 and the

Sarai grooves

21 and 31 can be referred to as an oil passage that supplies the refrigerating machine oil R to the vane groove 59.

Each vane groove 59 is formed so as to penetrate to both end faces 55a and 55b of the rotor 50, and is open at these both end faces 55a and 55b.

During the period in which the vane groove 59 opened in the end surface 55a of the rotor 50 is located within the rotation angle range α in which the

Sarai grooves

21 and 31 are formed, the Sarai groove 21 and the vane groove 59 communicate with each other. The refrigerating machine oil R is supplied from the salai groove 21 to the vane groove 59.

On the other hand, when the vane groove 59 is in the rotation angle range β (other rotation angle range) excluding the rotation angle range α in which the

Sarai grooves

21 and 31 are formed, the

Sarai grooves

21 and 31 and the vane groove 59 are provided. And the supply of the refrigerating machine oil R from the

Sarai grooves

21 and 31 to the vane groove 59 is shut off, and the vane groove 59 becomes a closed space.

The refrigerating machine oil R supplied to the vane groove 59 from the

Sarai grooves

21 and 31 becomes a back pressure that causes the vane 58 to protrude toward the inner peripheral surface 41 of the cylinder 40.

Here, the refrigerating machine oil R supplied to the Sarai groove 31 of the rear side block 30 is very much between the bearing 37 of the rear side block 30 and the outer peripheral surface of the rotating shaft 51 supported by the bearing 37 from the oil passage 34a. It has passed through a narrow gap.

The refrigerating machine oil R has a high pressure (discharge pressure Pd) corresponding to the high pressure atmosphere in the discharge chamber 14 in the oil passage 34a, but reaches the salai groove 31 due to a pressure loss while passing through this narrow gap. In this case, the pressure Pm is lower than the discharge pressure Pd inside the discharge chamber 14, which is an intermediate pressure Pm.

Here, the intermediate pressure Pm is a pressure higher than the pressure of the refrigerant gas G (low pressure Ps) in the suction chamber 13 and lower than the pressure of the refrigerant gas G (discharge pressure Pd) in the discharge chamber 14 (Ps <Pm). <Pd).

Similarly, the passage through which the refrigerating machine oil R passes between the oil passage 24 of the front side block 20 and the Sarai groove 21 is the bearing 27 of the front side block 20 and the outer peripheral surface of the rotary shaft 51 supported by the bearing 27. It is a very narrow gap between.

The refrigerating machine oil R has a high pressure (discharge pressure Pd) corresponding to the high pressure atmosphere in the discharge chamber 14 in the oil passage 24, but when it reaches the Saray groove 21 due to a pressure loss while passing through this narrow gap. Is a pressure (intermediate pressure Pm) lower than the discharge pressure Pd inside the discharge chamber 14.

Therefore, the back pressure that is supplied from the

Sarai grooves

21 and 31 to the vane groove 59 and causes the vane 58 to protrude toward the inner peripheral surface 41 of the cylinder 40 is the intermediate pressure Pm.

As described above, the

Sarai grooves

21 and 31 are formed corresponding to a range (rotational angle range α) from when the compression chamber 43 is in the suction stroke until it approaches the final stage of the compression stroke. In this case, since the pressure inside the compression chamber 43 is at most the medium pressure Pm, the back pressure of the vane 58 is insufficient due to the refrigerating machine oil R having the medium pressure Pm supplied from the

Sarai grooves

21 and 31 to the vane groove 59. Never do.

On the other hand, when the vane groove 59 shifts to the rotation angle range β beyond the rotation angle range α in which the

Sarai grooves

21 and 31 are formed, the vane groove 59 does not communicate with the

Sarai grooves

21 and 31 and is frozen. Supply of machine oil R was shut off and filled with supplied refrigerating machine oil R (including not only a state where it was completely filled with refrigerating machine oil R but also a state where refrigerant gas G was slightly mixed) It becomes space. When the vane 58 enters the bottom side of the vane groove 59 as the compression proceeds, the closed space in the vane groove 59 is in a substantially liquid compression state.

In the liquid compression state, since a high pressure Ph (Pd <Ph) exceeding the discharge pressure Pd inside the discharge chamber 14 is obtained, this high pressure Ph can be supplied as the back pressure of the vane 58.

Here, the rotation angle range β corresponds to the range from the position approaching the end of the compression stroke (the angular position at which the compression chamber 43 starts to face the sub-discharge section 46) to the discharge stroke. For this reason, in this range, the pressure inside the compression chamber 43 starts to exceed the intermediate pressure Pm, and the back pressure acting on the vane 58 is maintained at the intermediate pressure Pm if the vane groove 59 continues to communicate with the

Sarai grooves

21 and 31. If this is the case, the vane 58 may chatter due to the pressure inside the compression chamber 43.

In particular, in the case of a vane rotary type compressor that performs only one cycle of the refrigerant gas suction stroke, compression stroke, and discharge stroke during one rotation of the rotor 50 as in the compressor 1 of the present embodiment, per rotor 50 rotation. The length of the compression stroke is longer than that in which the suction stroke, the compression stroke, and the discharge stroke are performed in two cycles. For this reason, as shown in FIG. 2, when the preceding compression chamber 43A is at the end of the compression stroke, the inside of the compression chamber 43B following the compression chamber 43A is also at a relatively high pressure.

Moreover, in the compressor 1 of the present embodiment, the remote portion 49 is formed to be biased to the upstream side of the rotation direction W with respect to the proximity portion 48, and specifically, the rotation direction from the remote portion 49 to the proximity portion 48. The angle along W is set as wide as 270 degrees or more. For this reason, the length of the compression stroke is further increased, and the internal pressures of the two

compression chambers

43A and 43B that are adjacent to each other tend to be close to the discharge pressure Pd.

As a result, the vane 58 that partitions both the

compression chambers

43A and 43B (in FIG. 2, the vane 58A on the upstream side of the preceding compression chamber 43A) has a high direction opposite to the back pressure (the bottom direction of the vane groove 59). Pressure becomes easy to act. For this reason, the vane 58A may chatter, resulting in a decrease in efficiency and a problem such as abnormal noise.

However, as described above, in the compressor 1 of the present embodiment, in the rotation angle range β, the vane groove 59 is a closed space substantially filled with the refrigerating machine oil R having the medium pressure Pm, and the vane groove 59 as the compression proceeds. The entry amount of the vane 58 entering the bottom side in 59 increases. Then, as the amount of entry of the vane 58 increases, the pressure inside the vane groove 59 in the substantially liquid compression state rapidly increases. For this reason, when the compression proceeds to such an extent that the pressures in the

compression chambers

43A and 43B both become high pressures of about the discharge pressure Pd, the back pressure acting on the vane 58A causes the discharge pressures Pd of the

compression chambers

43A and 43B to be reduced. The pressure Ph exceeds (Pd <Ph).

Thus, at the end of the compression stroke, the state where the tip of the vane 58A slides stably without being separated from the inner peripheral surface 41 of the cylinder 40 is maintained, so that the vane 58A can be prevented from chattering. .

As described above, according to the compressor 1 according to the present embodiment, at the end of the compression stroke, the pressure inside the compression chambers 43 (

compression chambers

43A and 43B in FIG. 2) reaches a high pressure of about the discharge pressure Pd. Even in this case, the pressure Ph exceeding the discharge pressure Pd can be supplied as the back pressure to the vane 58 (the vane 58A in FIG. 2).

Moreover, in the compressor 1 according to the present embodiment, the pressure inside the compression chamber 43 increases as the compression proceeds. However, as the compression proceeds, the amount of the vane 58 entering the vane groove 59 increases, and the vane 58 becomes the vane. It is pushed down to the bottom side of the groove 59. As a result, the pressure inside the vane groove 59 (back pressure of the vane 58) also increases, so that the increase in the pressure inside the compression chamber 43 and the increase in the back pressure of the vane 58 are always associated with each other. it can.

<Embodiment 2>
The compressor 1 of the first embodiment described above is a space in which the vane groove 59 is closed in other rotation angle ranges β except for the predetermined rotation angle range α. In α, a refrigerating machine oil R having a medium pressure Pm is supplied. Therefore, the pressure inside the vane groove 59 at the time when the vane groove 59 is closed is the intermediate pressure Pm. Therefore, the starting point of the increase in the back pressure due to the liquid compression of the refrigerator oil R is the intermediate pressure Pm.

The compressor of the second embodiment has the same configuration as the compressor 1 of the first embodiment shown in FIGS. 1 and 2 except that both side blocks 20 and 30 are changed from those shown in FIG. 3 to those shown in FIG. The structure is redundant and redundant description is omitted.

As shown in FIG. 4, the rear side block 30 has a rotation angle of the Sarai groove 31 (21) along which the refrigerating machine oil R of medium pressure Pm is supplied along the rotation direction W of the rotor 50 (see FIG. 2). A high-pressure oil passage 32 (22) for supplying the refrigerating machine oil R corresponding to the discharge pressure Pd inside the discharge chamber 14, which is different from the Sarai groove 31 (21), is additionally formed at a position exceeding the range α. ing.

Although FIG. 4 shows the rear side block 30, the front side block 20 can be expressed substantially symmetrically with respect to the rear side block 30. Therefore, the Sarai groove 21 and the high-pressure oil passage 22 are also formed in the front side block 20 as in FIG.

The positions where the high-

pressure oil passages

22 and 32 are formed are the width of the vane groove 59 from the downstream end edge of the

Sarai grooves

21 and 31 along the rotation direction W of the rotating shaft 51 or slightly more than this width. It is a position separated by a large length.

That is, when the vane groove 59 of the rotor 50 rotating along the rotation direction W is positioned in the rotation angle range α (from the time when the compression chamber 43 is in the suction stroke, the end of the compression stroke is approached (the compression chamber is compressed). In the range up to the angular position) where 43 starts to face the sub-discharge portion 46, the refrigerating machine oil R of medium pressure Pm is supplied to the vane groove 59 as in the first embodiment. When the vane groove 59 passes through the rotation angle range α, the vane groove 59 is instantaneously closed, but immediately thereafter, the vane groove 59 leads to the high-

pressure oil passages

22 and 32. In the rotational angle range γ where the groove 59 and the high-

pressure oil passages

22 and 32 communicate with each other, high-pressure (discharge pressure Pd) refrigerating machine oil R is supplied to the vane groove 59.

The high-

pressure oil passages

22 and 32 are, for example, branched from the oil passages 24 and 34 a and communicated with the Sarai grooves 21 and 31 (gap between the

bearings

27 and 37 and the outer peripheral surface of the rotating shaft 51). It opens to inner surface 25, 35 (refer FIG. 1) of both the side blocks 20 and 30 by another path | route.

Accordingly, the high-

pressure oil passages

22 and 32 have no pressure loss in the gap between the

bearings

27 and 37 and the outer peripheral surface of the rotary shaft 51, so that the refrigerating machine oil R having the discharge pressure Pd that is the atmospheric pressure of the discharge chamber 14 is supplied. The vane groove 59 can be supplied.

The high pressure (discharge pressure Pd) refrigerating machine oil R is supplied to the vane groove 59 and the time from when the vane groove 59 passes the rotation angle range γ until the next time the vane groove 59 communicates with the

salai grooves

21 and 31. When in the rotation angle range β, the vane groove 59 is a closed space.

Therefore, in the compressor of the second embodiment, when the vane groove 59 is in the rotation angle range β, the inside of the vane groove 59 is in a liquid compression state, and the both side blocks 20 and 30 shown in FIG. In some cases, a back pressure of a higher pressure Ph ′ (Pd <Ph <Ph ′) can be supplied to the vane 58. In the compressor of the second embodiment, as described above, the pressure inside the vane groove 59 at the time when the vane groove 59 is closed is set to the discharge pressure Pd higher than the intermediate pressure Pm. it can.

Therefore, in the compressor of the second embodiment, the very high pressure Ph ′ supplied as the back pressure of the vane 58 is set to a pressure higher than the pressure Ph supplied as the back pressure of the vane 58 in the first embodiment. be able to.

Thus, even when a pressure higher than the pressure Ph exceeding the discharge pressure Pd is required as the back pressure of the vane 58, it is possible to appropriately cope with chattering.

The high-

pressure oil passages

22 and 32 are formed at positions away from the downstream side edge of the

Sarai grooves

21 and 31 by the width of the vane groove 59 or a length slightly larger than this width. Through the groove 59, the

Sarai grooves

21 and 31 to which the medium pressure Pm refrigerating machine oil R is supplied communicate with the high

pressure oil passages

22 and 32 to which the high pressure (discharge pressure Pd) refrigerating machine oil R is supplied. This is to prevent it.

<Embodiment 3>
In the first embodiment described above, the pressure Ph exceeding the discharge pressure Pd is supplied to the vane 58 as the back pressure at the end of the compression stroke. In the second embodiment described above, a pressure Ph ′ that is higher than the pressure Ph is supplied to the vane 58 as a back pressure.

Therefore, at the end of the compression stroke, the tip of the vane 58 can be held in a stable sliding state without leaving the inner peripheral surface 41 of the cylinder 40. However, for example, if the back pressure applied to the vane 58 is further increased due to, for example, a change in the viscosity of the refrigerating machine oil R, the pressing load on the inner peripheral surface 41 of the cylinder 40 at the tip of the vane 58 may be excessive. As described above, when the pressing load on the inner peripheral surface 41 of the cylinder 40 at the tip of the vane 58 becomes excessive, the tip of the vane 58 is damaged due to wear, or unnecessary power is required when the rotor 50 is driven to rotate, resulting in operating efficiency. Decreases.

Therefore, in the present embodiment, as shown in FIG. 5, the entire surface of the inner peripheral surface 41 of the cylinder 40 is in the entire range between the vicinity of the end of the compression process and the vicinity of the proximity portion 48 along the rotation direction W of the rotor 50. Fine recesses A (see FIG. 6) are formed by well-known shot peening.

Specifically, in the case of the first embodiment, the formation range of the fine recesses A on the surface of the inner peripheral surface 41 of the cylinder 40 is such that the vane groove 59 is the salais of both side blocks 20 and 30 as shown in FIG. Corresponding to the range of the rotation angle range β beyond the rotation angle range α in which the

grooves

21 and 31 are formed (the range where the vane groove 59 is positioned in the rotation angle range α). Then, the fine recess A is not formed). That is, the formation range of the fine recess A corresponds to the closed space range in which the vane groove 59 is substantially filled with the refrigerating machine oil R of medium pressure Pm, and the back pressure acting on the vane 58 causes the discharge pressure Pd to be reduced. This is the region where the pressure Ph exceeds.

Further, in the case of the second embodiment, the formation range of the fine recesses A on the surface of the inner peripheral surface 41 of the cylinder 40 is such that the vane groove 59 is the salai groove 21 of both side blocks 20 and 30 as shown in FIG. , 31 exceeds the rotation angle range α formed and passes through the rotation angle range γ communicated with the high-

pressure oil passages

22, 32 to the rotation angle range from the point where the rotation angle reaches the

salai grooves

21, 31. This corresponds to a range of β (in the range where the vane groove 59 is located in the rotation angle range α and the rotation angle range γ, the fine recess A is not formed). That is, the formation range of the fine recess A corresponds to the range of the closed space in which the vane groove 59 is in the liquid compression state with the refrigerating machine oil R having the medium pressure Pm, and the back pressure acting on the vane 58 is higher pressure Ph ′. This is the area.

As shown in FIG. 6, the fine recess A on the surface of the inner peripheral surface 41 of the cylinder 40 causes a large number of hard shot materials having a particle size of several μm to several tens of μm to collide with the surface of the inner peripheral surface 41 at high speed. The surface layer portion is work-hardened. The shot material used is preferably molybdenum disulfide powder having high lubricating performance as a solid lubricant.

Thus, by forming the fine concave portion A by shot peening, an oil reservoir is formed in the range where the fine concave portion A is formed on the surface of the inner peripheral surface 41 of the cylinder 40. Therefore, even when the pressing load on the inner peripheral surface 41 of the cylinder 40 at the tip of the vane 58 becomes excessive, the refrigerating machine oil mixed with the refrigerant gas in the compression chamber 43 accumulates in the fine recess A, and the inner periphery of the cylinder 40 The lubricity of the tip of the vane 58 sliding with respect to the surface 41 can be improved.

Therefore, wear at the tip of the vane 58 is suppressed, and furthermore, useless power loss can be reduced when the rotor 50 is driven to rotate.

In addition, the formation range of the fine recesses A is formed so that the vane groove 59 is formed corresponding to only the range of the closed space in the liquid compression state with the refrigerating machine oil R having the medium pressure Pm. It is not necessary to provide the entire circumference, and the working time can be shortened and the working cost can be reduced.

<Embodiment 4>
In the compressor 1 according to the first embodiment, as described above, in the vicinity of the end of the compression stroke (from immediately before and immediately after the discharge stroke), the pressures in both the

compression chambers

43A and 43B are both substantially equal to the discharge pressure Pd. As the compression proceeds, the pressure in the substantially liquid-compressed vane groove 59 increases, and the back pressure (vane back pressure) acting on the vane 58 can be significantly increased.

FIG. 7A shows changes in the vane back pressure (a in the figure) acting on the vane 58 and changes in the pressure in the compression chamber 43 (b in the figure) in the intake stroke, compression stroke, and discharge stroke of the compressor 1 described above. It is a figure. 7A, Pd is the discharge pressure (high pressure) value, and Ps is the pressure (low pressure) value of the refrigerant gas sucked into the compression chamber 43.

In FIG. 7A, the rotation angle of the rotor 50 is near 0 degrees (360 degrees) when the vane 58 is positioned near the proximity portion 48 along the rotation direction W of the compression chamber 43 (the discharge stroke and the discharge stroke). During the suction stroke), the rotor 50 makes one rotation (the rotation angle is 0 to 360 degrees), whereby the one-stroke suction stroke, compression stroke, and discharge stroke are performed.

As shown in FIG. 7A, the back pressure (vane back pressure) acting on the vane 58 rises from near the end of the compression stroke (rotation angle of the rotor 50 is around 270 degrees), and immediately before the discharge stroke (rotation of the rotor 50). The pressure Ph is reached at an angle of around 355 degrees.

By increasing the vane back pressure as described above, the tip of the vane 58 can be satisfactorily brought into contact with the inner peripheral surface of the cylinder 40, but in the vicinity of the end of the compression stroke (from immediately before and immediately after the discharge stroke). Then, since the pressure Ph that is significantly higher than the pressure in the compression chamber 43 (about the discharge pressure Pd) acts as the vane back pressure, the tip of the vane 58 abuts the inner peripheral surface of the cylinder 40 more strongly than necessary. There is.

In particular, immediately before and after the discharge stroke, a part of the high-pressure refrigerant gas in the compression chamber 43 is discharged from the discharge hole 45b, so that the pressure in the compression chamber 43 rapidly decreases, and the vane 58 The tip end comes into stronger contact with the inner peripheral surface of the cylinder 40.

Thus, in a situation where the tip of the vane 58 is in contact with the inner peripheral surface of the cylinder 40 more than necessary immediately before and after the discharge stroke, contact between the tip of the vane 58 and the inner peripheral surface of the cylinder 40 is achieved. Since the resistance becomes larger than necessary, useless power is required when the rotor 50 is rotationally driven, and the operation efficiency is lowered.

Therefore, in this embodiment, as shown in FIG. 8, a throttle hole 80 for releasing a part of the back pressure is formed in the inner surface 35 of the rear side block 30. The throttle hole 80 is in the rotation angle range β excluding the rotation angle range α in which the salai groove 31 is formed, and is near the end of the compression stroke (near the discharge stroke in the main discharge portion 45). It is formed corresponding to the region.

As shown in FIGS. 9A and 9B, the throttle hole 80 communicates with the oil discharge port 81 formed in the outer surface 36 of the rear side block 30 through a passage 82. In the present embodiment, the passage 82 is included in a part of the throttle hole 80, and the throttle hole 80 and the passage 82 constitute the entire throttle hole.

9A and 9B, an oil separator (not shown) is installed at the oil discharge port 81 of the outer surface 36 of the rear side block 30. The oil discharge port 81 communicates with the discharge path 38 via an oil flow path groove 83.

As shown in FIG. 10, in the vicinity of the end of the compression stroke (from immediately before and immediately after the discharge stroke), the throttle hole 80 communicates with the bottom 59 a in the vane groove 59. When the throttle hole 80 and the bottom 59a in the vane groove 59 are communicated with each other near the end of the compression stroke, the refrigerating machine oil R (refrigerant gas is mixed) is supplied to the bottom 59a in the vane groove 59 and is in a liquid compression state. A part of the oil is discharged from the throttle hole 80 through the passage 82 to the oil separator 70 (see FIG. 1) from the oil discharge port 81. The refrigerating machine oil discharged to the oil separator 70 is returned to the bottom in the discharge chamber 14.

In this way, when a part of the refrigerating machine oil R in the liquid compression state is discharged from the throttle hole 80 to the oil separator 70 side through the passage 82, as shown in FIG. 7B, the pressure rises immediately before and immediately after the discharge stroke. The vane back pressure (a in the figure) is reduced. Therefore, it is possible to suppress the tip of the vane 58 from coming into contact with the inner peripheral surface of the cylinder 40 more than necessary in the vicinity immediately before and immediately after the discharge stroke, so that it is possible to reduce unnecessary power loss when the rotor 50 is rotationally driven. .

In the fourth embodiment, a part of the refrigerating machine oil that is supplied to the bottom 59a in the vane groove 59 and is in a liquid compressed state passes through the passage 82 in the rear side block 30 from the throttle hole 80 to the oil separator 81. 70 (discharge chamber 14), the same hole is formed on the front side block 20 side, and the hole is discharged from the hole to the suction chamber 13 through a passage formed in the front side block 20. It may be.

<Embodiment 5>
In the compressor 1 according to the first embodiment, as described above, in the vicinity of the end of the compression stroke (from immediately before and immediately after the discharge stroke), the pressures in both the

compression chambers

As shown in FIG. 7A, the back pressure (vane back pressure) acting on the vane 58 increases from the vicinity of the end of the compression stroke (rotation angle of the rotor 50 is about 270 degrees), and immediately before the discharge stroke (the rotation of the rotor 50). The pressure Ph is reached at a rotation angle of around 355 degrees.

Therefore, in this embodiment, as shown in FIG. 11, a hole 100 for releasing a part of the back pressure is formed in the inner surface 35 of the rear side block 30. This hole 100 is a region that is in the vicinity of the end of the compression stroke (near the immediately before the discharge stroke in the main discharge portion 45) in the rotation angle range β excluding the rotation angle range α in which the salai groove 31 is formed. It is formed corresponding to.

In the present embodiment, the hole 100 further has a discharge stroke in the main discharge section 45 from the vicinity of the final stage of the compression stroke within a rotation angle range β excluding the rotation angle range α in which the salai groove 31 is formed. It is provided near one end (in the vicinity of the right end of the communication groove 81 in FIG. 11) in the concave communication groove 84 formed corresponding to the nearby region. FIG. 12 shows the positional relationship among the hole 100, the communication groove 84, and the vane groove 59.

As shown in FIGS. 13A and 13B, the hole 100 communicates with the oil discharge port 81 formed in the outer surface 36 of the rear side block 30 through the passage 82. In the present embodiment, the passage 82 is included in a part of the hole 100, and the hole 100 and the passage 82 constitute the whole hole.

13A and 13B, an oil separator (not shown) is installed at the oil discharge port 81 on the outer surface 36 of the rear side block 30. The oil discharge port 81 communicates with the discharge path 38 through an oil passage groove 83.

Also, a trigger valve type pressure regulating valve (hereinafter referred to as “first relief valve”) 85 is disposed in the large diameter portion formed on the oil discharge port 81 side of the passage 82. The first relief valve 85 includes a spherical valve body 86 and a spring member 87, and normally the valve body 86 is urged by the urging force (spring force) of the spring member 87 to close the small diameter side of the passage 82. The valve is closed.

The first relief valve 85 has a pressure between the vane groove 59 (vane back pressure) and a discharge pressure (a discharge pressure of high-pressure gas (refrigerant gas) discharged into the discharge chamber 14 through the discharge path 38 in the discharge stroke). When the differential pressure is equal to or lower than a predetermined pressure Pa (<Ph), the valve is closed. When the differential pressure is equal to or higher than the predetermined pressure Pa, the valve is opened against the biasing force of the spring member 87. It is configured as follows.

As shown in FIGS. 12 and 14, the communication groove 84 communicates with the bottom 59 a in the vane groove 59 from the vicinity of the end of the compression stroke to the vicinity of the end of the compression stroke (nearly immediately after the discharge stroke). It is in a positional relationship. As a result, the hole 100 is in communication with the bottom 59a in the vane groove 59 through the communication groove 84, so that one of the vane back pressures (refrigerating machine oil R supplied to the bottom 59a in the vane groove 59 and in a liquid compression state). The portion is discharged from the hole 100 to the passage 82 side.

The first relief valve 85 is opened against the urging force of the spring member 87 when the differential pressure becomes a predetermined pressure Pa or more, and a part of the refrigerating machine oil R in the liquid compression state is oil discharge port 81. To the oil separator 70 (see FIG. 1). The refrigerating machine oil discharged to the oil separator 70 is returned to the bottom in the discharge chamber 14. And in a discharge process, since a vane back pressure falls, the 1st relief valve 85 will be in a valve closing state.

As described above, when the first relief valve 85 is opened and a part of the refrigerating machine oil R in the liquid compression state is discharged from the hole 100 to the oil separator 70 side through the passage 82, it is shown in FIG. As described above, the vane back pressure (a in the figure) increased from immediately before to immediately after the discharge stroke is reduced to a predetermined pressure Pa. Therefore, it is possible to suppress the tip of the vane 58 from coming into contact with the inner peripheral surface of the cylinder 40 more than necessary in the vicinity immediately before and immediately after the discharge stroke, so that it is possible to reduce unnecessary power loss when the rotor 50 is rotationally driven. .

<Embodiment 6>
In the sixth embodiment, as shown in FIG. 16, a hole 101 for releasing a part of the back pressure is formed in the inner surface 35 of the rear side block 30. This hole 101 is a region that is in the rotation angle range β excluding the rotation angle range α in which the salai groove 31 is formed, and is near the end of the compression stroke (near the discharge stroke in the main discharge portion 45). It is formed corresponding to.

In the present embodiment, the hole 101 is in the vicinity of the discharge stroke at the main discharge portion 45 from the vicinity of the end of the compression stroke within the rotation angle range β excluding the rotation angle range α in which the saray grooves 31 are formed. It is provided in the vicinity of the other end in the concave communication groove 84 formed corresponding to the region (in FIG. 16, in the vicinity of the left end of the communication groove 84).

As shown in FIGS. 17A and 17B, the hole 101 communicates with the outer surface 36 (that is, the discharge chamber 14: see FIG. 1) through a passage 82a formed in the rear side block 30. In the present embodiment, the passage 82a is included in a part of the hole 110, and the hole 110 and the passage 82a constitute the entire hole.

In FIGS. 17A and 17B, an oil separator (not shown) is installed at the oil discharge port 81 of the outer surface 36 of the rear side block 30. Further, the oil discharge port 81 communicates with the discharge path 38 via the oil flow path groove 83.

Further, a reed valve type pressure regulating valve (hereinafter referred to as “second relief valve”) 88 is disposed in a region where the passage 82a of the outer surface 36 of the rear side block 30 communicates. The base end side of the second relief valve 88 is fixed to the outer surface 36 by a fixing screw 88a, and is normally in a closed state in which the passage 82a is closed by the urging force (elastic force) of the second relief valve 88.

The second relief valve 88 is a pressure between the pressure in the vane groove 59 (vane back pressure) and the discharge pressure (discharge pressure of the high-pressure gas (refrigerant gas) discharged into the discharge chamber 14 through the discharge path 38 in the discharge stroke). The valve is operated with a differential pressure, and when the differential pressure is less than or equal to a predetermined pressure Pa (<Ph), the valve is closed, and when the differential pressure exceeds the predetermined pressure Pa, the valve is opened.

As in the fifth embodiment, the positional relationship is such that the communication groove 84 communicates with the bottom 59a in the vane groove 59 from the vicinity of the end of the compression stroke to the vicinity of the end of the compression stroke (from immediately before to immediately after the discharge stroke). is there. Accordingly, since the hole 101 is in communication with the bottom 59a in the vane groove 59 through the communication groove 84, one of the vane back pressures (refrigerating machine oil R supplied to the bottom 59a in the vane groove 59 and in a liquid compression state). The portion is discharged from the hole 101 toward the passage 82a.

The second relief valve 88 is opened when the differential pressure exceeds a predetermined pressure Pa, and a part of the refrigerating machine oil R in the liquid compression state passes through the passage 82a to the outer surface 36 of the rear side block 30 (that is, the discharge pressure). To the chamber 14). In addition, since the vane back pressure is reduced in the discharge stroke, the second relief valve 88 is closed.

As described above, when the second relief valve 88 is opened and a part of the refrigerating machine oil R in the liquid compression state is discharged from the hole 101 to the discharge chamber 14 side through the passage 82a, it is shown in FIG. As described above, the vane back pressure (a in the figure) increased from immediately before to immediately after the discharge stroke is reduced to a predetermined pressure Pa. Therefore, it is possible to suppress the tip of the vane 58 from coming into contact with the inner peripheral surface of the cylinder 40 more than necessary in the vicinity immediately before and immediately after the discharge stroke, so that it is possible to reduce unnecessary power loss when the rotor 50 is rotationally driven. .

Cross-reference of related applications

This application includes Japanese Patent Application No. 2013-241196 filed with the Japan Patent Office on November 21, 2013, Japanese Patent Application No. 2012-283142 filed with the Japan Patent Office on December 26, 2012, and 2012 Claiming priority based on Japanese Patent Application No. 2012-283143 filed with the Japan Patent Office on December 26, the entire disclosure of which is fully incorporated herein by reference.

Claims

A rotor formed with a substantially cylindrical vane groove that rotates about an axis, a cylinder having a contoured inner peripheral surface that surrounds the rotor from the outside of the outer peripheral surface, and a predetermined groove. A plurality of plate-like vanes provided so as to be protruded toward the inner peripheral surface of the cylinder in response to back pressure due to refrigerating machine oil supplied from the oil passage to the vane groove, and A compressor body in which a compression chamber is formed to compress at a rate of once during one rotation of the rotor is provided inside the housing;
The oil passage communicates with the vane groove in a predetermined rotation angle range of the rotor, and the vane groove is in a rotation angle range other than a rotation angle range in which the oil passage communicates with the vane groove. A gas compressor characterized by being a closed space.
The said oil path is formed so that the refrigerating machine oil corresponding to the intermediate pressure which restrict | squeezed the pressure of the gas discharged from the said compression chamber in the said rotation angle range may be supplied. Gas compressor.
The oil passage is formed to supply refrigerating machine oil corresponding to an intermediate pressure obtained by reducing the pressure of the gas discharged from the compression chamber in the rotation angle range,
Corresponding to the pressure of the gas discharged from the compression chamber, which is different from the oil passage supplying the refrigerating machine oil corresponding to the intermediate pressure at a position exceeding the rotation angle range along the rotation direction of the rotor. A high-pressure oil passage for supplying refrigeration oil is formed,
The other rotation angle range is a rotation angle range excluding a rotation angle range in which the oil passage communicates with the vane groove and a rotation angle range in which the high pressure oil passage communicates with the vane groove. The gas compressor according to claim 1.
The compressor body has two side blocks that touch both end faces of the rotor and the cylinder and cover the both end faces,
The vane groove is formed to open at an end surface of the rotor,
The oil passage is formed to open in a portion of the side block that faces the end surface of the rotor,
4. The device according to claim 1, wherein the rotation is switched between a state where the opening of the oil passage and the opening of the vane groove communicate with each other and the state where the opening of the vane groove does not communicate with the rotation of the rotor. The gas compressor according to one item.
Of the inner peripheral surface of the cylinder, the remote portion having the maximum distance from the outer peripheral surface of the rotor is located at a position biased to the upstream side in the rotational direction of the rotor with respect to the proximity portion having the minimum distance. It forms, The gas compressor as described in any one of Claim 1 thru | or 4 characterized by the above-mentioned.
6. A minute recess is formed in a region of an inner peripheral surface of the cylinder corresponding to the other rotation angle range, in which the vane groove is a closed space. A gas compressor according to claim 1.
The gas compressor according to claim 6, wherein the fine recess is formed by shot peening.
The gas compressor according to claim 7, wherein the shot material used in the shot peening is molybdenum disulfide powder.
From the initial stage of the compression stroke to a predetermined range, the oil passage communicates with the vane groove and refrigeration oil having a predetermined pressure is supplied into the vane groove.
From the predetermined range of the compression stroke to the vicinity immediately before the discharge stroke, the vane groove is shielded from the oil passage to form a sealed space. Increase the pressure,
2. The gas compressor according to claim 1, further comprising a throttle hole for letting a part of the increased back pressure in the vane groove to the outside.
10. The gas compressor according to claim 9, wherein the throttle hole communicates with a discharge pressure space side from which high-pressure gas compressed in the compression stroke is discharged.
An oil separator that separates oil from the high-pressure gas discharged into the discharge pressure space is provided, and the throttle hole communicates with a discharge port side of the high-pressure gas to the oil separator. The gas compressor according to claim 9.
From the initial stage of the compression stroke to a predetermined range, the oil passage communicates with the vane groove and refrigeration oil having a predetermined pressure is supplied into the vane groove.
From the predetermined range of the compression stroke to the vicinity immediately before the discharge stroke, the vane groove is shielded from the oil passage to form a sealed space. Increase the pressure,
Furthermore, it has a hole for releasing a part of the back pressure that has been boosted in the vane groove to the outside,
The gas compressor according to claim 1, wherein a valve body capable of opening and closing the hole is disposed in a passage communicating with the hole or on an end surface of the hole.
The discharge pressure space into which the high-pressure gas compressed in the compression stroke is discharged includes an oil separator that separates oil from the high-pressure gas discharged into the discharge pressure space, and the hole is connected to the oil separator. Communicating with the high-pressure gas outlet side of
The valve body is operated by a differential pressure between the pressure in the vane groove and the discharge pressure of the high-pressure gas discharged to the discharge pressure space side in the discharge stroke, and when the differential pressure is equal to or lower than a predetermined pressure, the valve body is closed. The gas compressor according to claim 12, wherein when the differential pressure becomes equal to or higher than the predetermined pressure, the valve is opened.
The hole communicates with the discharge pressure space side from which the high-pressure gas compressed in the compression stroke is discharged,
The valve body is operated by a differential pressure between the pressure in the vane groove and the discharge pressure of the high-pressure gas discharged to the discharge pressure space side in the discharge stroke, and when the differential pressure is equal to or lower than a predetermined pressure, the valve body is closed. The gas compressor according to claim 12, wherein when the differential pressure becomes equal to or higher than the predetermined pressure, the valve is opened.
The gas compressor according to claim 13, wherein the valve body is a relief valve of a trigger valve type.
The gas compressor according to claim 14, wherein the valve body is a reed valve type relief valve.