WO2013183609A1

WO2013183609A1 - Gas compressor

Info

Publication number: WO2013183609A1
Application number: PCT/JP2013/065413
Authority: WO
Inventors: 津田　昌宏; 博匡島口; 尾崎　達也; 幸治廣野; 士津真金子
Original assignee: カルソニックカンセイ株式会社
Priority date: 2012-06-05
Filing date: 2013-06-03
Publication date: 2013-12-12
Also published as: JP2014013035A; JP5913199B2

Abstract

Provided is a gas compressor that is able to prevent excess compression from occurring in a compression chamber. A region (a proximal section (48)) in which the inner peripheral surface (40a) of a cylinder (40) and the outer peripheral (50a) of a rotor (50) are closest within a range of one circuit of the axis of a rotary shaft (51) has at least two discharge holes for discharging a refrigerant gas compressed in the compression chamber (43) on the upstream side in the direction of rotation of the rotor (50) in the circumferential direction of the inner peripheral surface (40a) of the cylinder (40). The discharge holes are linked on the discharge chamber (14) side, without providing a discharge valve to a first discharge hole (45a), which is on the side closest to the proximal section (48), among the discharge holes, said discharge valve opening when the pressure of a medium compressed in the compression chamber has reached a prescribed discharge pressure, and closing when the prescribed discharge pressure has not been reached.

Description

Gas compressor

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

For example, a vehicle such as an automobile is provided with an air conditioner for adjusting the temperature in the passenger compartment. Such an air conditioner has a loop-shaped refrigerant cycle in which refrigerant (cooling medium) is circulated, and this refrigerant cycle is provided with an evaporator, a compressor, a condenser, and an expansion valve in this order. Yes.

The compressor (compressor) of the air conditioner compresses the gaseous refrigerant (refrigerant gas) evaporated by the evaporator into high-pressure refrigerant gas and sends it to the condenser.

As such a compressor, a rotor having a plurality of vanes provided so as to protrude and be housed in a cylinder having a substantially elliptical inner peripheral surface, the tip of which is slidably in contact with the inner peripheral surface of the cylinder has been rotated. A vane rotary type compressor that is freely supported is known (for example, see Patent Document 1).

This vane rotary type compressor has a compression chamber whose volume changes due to sliding contact with the inner circumferential surface of the rotating vane as the rotor rotates, and through the suction port as the volume of the compression chamber increases. The refrigerant gas is sucked in, the sucked refrigerant gas is compressed as the volume of the compression chamber decreases, and the high-pressure refrigerant gas is discharged into the discharge chamber through the discharge port. Then, high-pressure refrigerant gas is sent from the discharge chamber to the condenser side.

The vane is slidably disposed in a slit-like vane groove exposed on the surface from the inside of the rotor. And this vane protrudes from the rotor surface by the back pressure (vane back pressure) by the oil supplied to the bottom of the vane groove through the vane back pressure space and the centrifugal force of the rotating rotor, and the tip of the vane Is maintained in contact with the inner peripheral surface of the cylinder.

JP 54-28008 A

By the way, in a vane rotary type compressor, since the refrigerant gas is rapidly compressed, overcompression is likely to occur in the compression chamber, and accordingly, power loss is increased or the pressure difference between adjacent compression chambers is increased. From other types of gas compressors (for example, rotary piston type compressors) because the refrigerant gas compressed from the compression chamber downstream in the rotation direction to the compression chamber upstream in the rotation direction is likely to leak. However, the efficiency (coefficient of performance or COP (Coefficient of Performance)) tended to be low.

Therefore, the present invention has been made in view of the above circumstances, and an object thereof is to provide a gas compressor capable of preventing the occurrence of over-compression in a compression chamber.

In order to solve the above-mentioned problems, an invention according to claim 1 is directed to a substantially columnar rotor that rotates integrally with a rotation shaft, and an inner periphery having a contour shape that surrounds the rotor from the outside of the outer peripheral surface of the rotor. A cylinder having a surface, a plurality of plate-like vanes provided in a vane groove formed in the rotor so as to protrude from an outer peripheral surface of the rotor toward an inner peripheral surface of the cylinder, and both ends of the rotor and the cylinder Each of the two side blocks, and the vane forms a plurality of compression chambers by partitioning a space formed between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor, Each of the formed compression chambers is a gas compressor in which the contour shape of the inner peripheral surface of the cylinder is set so that the medium is sucked, compressed, and discharged only during one cycle of the rotation of the rotor. The inner circumferential surface of the cylinder and the outer circumferential surface of the rotor were compressed in the compression chamber on the upstream side in the rotation direction of the rotor with respect to the region closest to the circumference of the circumference of the rotation shaft. There are at least two discharge holes for discharging the medium to the outside along the circumferential direction of the inner peripheral surface of the cylinder, and at least the side closest to the closest region of the discharge holes. The first discharge hole has a discharge valve that opens when the pressure of the medium compressed in the compression chamber reaches a predetermined discharge pressure, and closes when the pressure does not reach the predetermined discharge pressure. It is not provided, but is characterized by communicating with the outside.

The gas compressor according to claim 2 is compressed in a compression chamber facing the second discharge hole on the second discharge hole located on the upstream side in the rotation direction of the rotor from the first discharge hole. A discharge valve is provided that opens when the pressure of the medium reaches the predetermined discharge pressure and closes when the medium pressure does not reach the predetermined discharge pressure.

The gas compressor according to claim 3, wherein the first discharge hole reaches the predetermined discharge pressure during compressor operation, and the medium in the compression chamber facing the first discharge hole is always exposed to the outside. It is characterized by discharging.

The gas compressor according to claim 4 is compressed in the compression chamber facing the second discharge hole also on the second discharge hole located on the upstream side of the first discharge hole in the rotation direction of the rotor. The valve opens when the pressure of the medium reaches the predetermined discharge pressure, and is not provided with a discharge valve that closes when the pressure does not reach the predetermined discharge pressure, and communicates with the outside. It is said.

According to a fifth aspect of the present invention, when the medium to be compressed in the compression chamber partitioned by the two adjacent vanes substantially reaches the predetermined discharge pressure, the gas compressor on the front side of the two vanes is provided. The vane passes through the second discharge hole, and the medium in the compression chamber reaching the predetermined discharge pressure is discharged to the outside from the second discharge hole.

The gas compressor according to claim 6, wherein a part of the residual medium remaining in the compression chamber without being discharged from the second discharge hole is formed after the front vane passes through the first discharge hole. It is characterized by being discharged to the outside through one discharge hole.

According to the gas compressor of the present invention, the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor are in the circumferential direction of the inner peripheral surface of the cylinder with respect to the region that is closest to the outer periphery of the rotary shaft around one axis. And at least two discharge holes for discharging the medium compressed in the compression chamber to the outside on the upstream side in the rotation direction of the rotor, so that the pressure of the refrigerant gas in the compression chamber is the highest in the closest region. Even when a predetermined discharge pressure is reached in the stage before facing the discharge hole on the near side, the refrigerant gas in the compression chamber is more upstream in the rotational direction of the rotor than the discharge hole on the side closest to the closest area. Since it can be made to discharge from the discharge hole located in the side, the overcompression in which the pressure of the refrigerant gas in the compression chamber exceeds a predetermined discharge pressure can be prevented, and power loss can be suppressed.

Furthermore, at least the first discharge hole on the side closest to the closest region opens when the pressure of the medium compressed in the compression chamber reaches a predetermined discharge pressure, and reaches the predetermined discharge pressure. When there is no discharge valve, the discharge valve that closes the valve is not provided, so that a collision noise (noise) accompanying the opening and closing of the discharge valve does not occur, and the cost can be reduced by reducing the number of parts.

1 is a longitudinal sectional view showing a gas compressor (vane rotary type gas compressor) according to Embodiment 1 of the present invention. FIG. 2 is a sectional view taken along line AA in FIG. 1. The cross-sectional view which shows the gas compressor (Vane rotary type gas compressor) which concerns on Embodiment 2 of this invention. The cross-sectional view which shows the gas compressor (vane rotary type gas compressor) which concerns on Embodiment 3 of this invention.

Hereinafter, the present invention will be described based on illustrated embodiments.
<Embodiment 1>
1 is a longitudinal sectional view showing a vane rotary type gas compressor (hereinafter referred to as “compressor”) as a gas compressor according to Embodiment 1 of the present invention, and FIG. 2 is taken along line AA in FIG. It is a figure which shows the cross section along. Note that the compressor of the present embodiment is an electric type that incorporates an electric motor.

(Overall configuration and operation of compressor)
The illustrated compressor 100 is configured, for example, as a part of an air conditioning system (hereinafter referred to as an “air conditioning system”) that performs cooling by using the heat of vaporization of a cooling medium, and condensing that is another component of the air conditioning system. It is provided on the circulation path of the cooling medium together with a condenser, an expansion valve, an evaporator, etc. (all not shown). In addition, as such an air conditioning system, the air conditioning apparatus for adjusting the temperature in the vehicle interior of a vehicle (automobile etc.) is mentioned, for example.

The compressor 100 compresses the refrigerant gas as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas to the condenser of the air conditioning system. The condenser liquefies the compressed refrigerant gas and sends it to the expansion valve as a high-pressure liquid refrigerant. The high-pressure and liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange with the heat of vaporization.

As shown in FIG. 1, the compressor 100 has a configuration in which a motor 90 and a compressor main body 60 are accommodated in a housing 10 mainly composed of a main body case 11 and a front cover 12.

The main body case 11 has a substantially cylindrical shape, and is formed such that one end (right side in FIG. 1) of the cylindrical shape is closed, and the other end (left side in FIG. 1) is open. Has been.

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 a low-pressure refrigerant gas G1 is introduced into the suction chamber 13 from an evaporator (not shown) of the air conditioning system. On the other hand, a discharge port 11a for discharging the high-pressure refrigerant gas G2 obtained in the compressor main body 60 to a condenser (not shown) of the air conditioning system is formed in the discharge chamber 14 described later of the main body case 11.

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 rotor 90a.

The motor 90 drives the rotor 90a and the rotating shaft 51 to rotate around the axis by exciting the electromagnet of the stator 90b with the electric power supplied via the power connector 90c attached to the end face of the front cover 12. Let

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.

Although the compressor 100 of the present embodiment is an electric type as described above, the gas compressor according to the present invention is not limited to an electric type, and may be a mechanical type. If the compressor 100 of the present embodiment is of a mechanical type, instead of providing the motor 90, the rotating shaft 51 protrudes from the front cover 12 to the outside, and the front end of the protruding rotating shaft 51 is connected to the vehicle. What is necessary is just to set it as the structure provided with the pulley, the gearwheel, etc. which receive motive power transmission from this engine.

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 inserted into the main body case 11 by a fastening member 15 such as a bolt. It is fixed.

The compressor body 60 includes the rotating shaft 51 rotated by the motor 90, a substantially cylindrical rotor 50 that rotates integrally with the rotating shaft 51, and the rotor 50 outside the outer peripheral surface 50a (see FIG. 2). A cylinder 40 having a contour-shaped inner peripheral surface 40a surrounding from the side, five plate-like vanes 58 provided so as to protrude from the outer peripheral surface 50a of the rotor 50 toward the inner peripheral surface 40a of the cylinder 40, and the rotor 50 and two side blocks (front side block 20 and rear side block 30) that block both ends of the cylinder 40 are provided.

The rotary 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.

On the outer peripheral surfaces of the front side block 20 and the rear side block 30, sealing members such as O-rings are installed over the entire outer periphery, and the discharge chamber is formed in the main body case 11 on the rear side block 30 side. 14 and the main body case 11 on the front side block 20 side and the suction chamber 13 formed in the front cover 12 are partitioned with good airtightness.

The oil separation unit 70 is attached to the outer surface of the rear side block 30 so as to be positioned in the discharge chamber 14. The motor 90 is provided in the suction chamber 13 formed in the front cover 12.

In the compressor main body 60, as shown in FIG. 2, there is a single cylinder between the inner peripheral surface 40a of the cylinder 40, the outer peripheral surface 50a of the rotor 50, and both side blocks 20, 30 (see FIG. 1). A chamber 42 is formed.

Specifically, the inner peripheral surface 41a of the cylinder 40 and the outer peripheral surface 50a of the rotor 50 are only one place (proximal portion 48 in FIG. 2) within a range of one rotation (angle 360 degrees) around the axis of the rotating shaft 51. The contour shape of the inner peripheral surface 40a of the cylinder 40 is set so as to be in close contact (closest to the nearest), whereby the cylinder chamber 42 forms a single substantially crescent-shaped space.

Of the contour shape of the inner peripheral surface 40a of the cylinder 40, the proximity portion 48, which is the region where the inner peripheral surface 40a of the cylinder 40 and the outer peripheral surface 50a of the rotor 50 are closest, In this embodiment, the remote portion 49 is located at a position away from the remote portion 49, which is the farthest area from the outer peripheral surface 50a of the 50, along the rotational direction W (clockwise direction in FIG. 2) of the rotor 50 at an angle of about 270 degrees. Is set.

The contour shape of the inner peripheral surface 40a of the cylinder 40 is such that the distance between the outer peripheral surface 50a of the rotor 50 and the inner peripheral surface 40a of the cylinder 40 is monotonous from the remote portion 49 to the proximity portion 48 along the rotation direction W. The shape is set to decrease.

The vane 58 is slidably fitted in a vane groove 59 formed in the rotor 50, and protrudes outward from the outer peripheral surface 50 a of the rotor 50 by back pressure due to the refrigerating machine oil supplied to the vane groove 59.

The vane 58 divides the single cylinder chamber 42 into a plurality of compression chambers 43, and one compression chamber 43 is formed by the two vanes 58 that move back and forth along the rotation direction W of the rotor 50. The Therefore, in the present embodiment in which five vanes 58 are installed around the rotation shaft 51 at equal angular intervals of 72 degrees, five compression chambers 43 are formed.

The volume in the compression chamber 43 obtained by partitioning the cylinder chamber 42 by the vane 58 monotonously decreases along the rotation direction W from the remote portion 49 to the proximity portion 48. In FIG. 1, the vane 58 exposed to the cylinder chamber 42 is omitted.

The suction hole 23 (see FIG. 2) formed in the front side block 20 and leading to the suction chamber 13 faces the portion on the downstream side in the rotation direction of the rotor 50 with respect to the proximity portion 48 of the cylinder chamber 42.

On the other hand, on the inner peripheral surface 40a of the cylinder 40 upstream of the proximity portion 48 of the cylinder chamber 42 in the rotation direction of the rotor 50, the first discharge holes 45a and the first discharge holes 45a are arranged along the circumferential direction of the inner peripheral surface 40a. Two discharge holes 45b are formed. The one closer to the proximity portion 48 along the rotation direction W of the rotor 50 is the first discharge hole 45a, and the first discharge hole 45a is located upstream of the first discharge port 45a along the rotation direction W of the rotor 50. Two discharge holes 45b are formed.

The first and second discharge holes 45a and 45b communicate with

discharge chambers

46a and 46b as spaces formed between the outer peripheral surface of the cylinder 40 and the inner peripheral surface of the main body case 11, respectively. Further, the

discharge passages

30a and 30b communicating with the rear side block 30 between the

discharge chambers

46a and 46b and the oil separation portion 70 attached to the outer surface of the rear side block 30 (surface facing the discharge chamber 14). Is formed.

Two first and second discharge holes 45 a and 45 b formed on the inner peripheral surface 40 a of the cylinder 40 are formed along the width direction of the cylinder 40. Details of the first and second discharge holes 45a and 45b will be described later.

In each compression chamber 43, during one rotation of the rotor 50, the refrigerant gas is sucked through the suction hole 23, the refrigerant gas is compressed, and the refrigerant gas is discharged into the first and second discharge holes 45a and 45b in one cycle. The contour shape of the inner peripheral surface 40a of the cylinder 40 is set so as to perform only.

On the upstream side in the rotational direction of the rotor 50 with respect to the remote portion 49 of the cylinder chamber 42, the cylinder 40 has a gap so that the distance between the inner peripheral surface 40 a of the cylinder 40 and the outer peripheral surface 50 a of the rotor 50 increases rapidly from a small state. The contour shape of the inner peripheral surface 40 a is set, and in the angle range including the remote portion 49, the volume of the compression chamber 43 increases as the rotor 50 rotates in the rotation direction W, and the compression chamber passes through the suction hole 23. This is a stroke (intake stroke) in which the low-pressure refrigerant gas G <b> 1 is sucked into 43.

Next, the cylinder 40 is arranged such that the distance between the inner peripheral surface 40a of the cylinder 40 and the outer peripheral surface 50a of the rotor 50 gradually decreases toward the downstream side in the rotation direction of the rotor 50 with respect to the remote portion 49 of the cylinder chamber 42. A contour shape of the inner peripheral surface 40a is set, and in that range, the volume of the compression chamber 43 decreases with the rotation of the rotor 50, and the stroke in which the refrigerant gas in the compression chamber 43 is compressed (compression stroke) Become.

As the rotor 50 rotates, the gap between the inner peripheral surface 40a of the cylinder 40 and the outer peripheral surface 50a of the rotor 50 is further reduced, so that the compression of the refrigerant gas further proceeds, and the refrigerant gas pressure becomes a predetermined discharge pressure. When reaching, the high-pressure refrigerant gas G2 becomes a stroke (discharge stroke) discharged to the first discharge hole 45a (and the second discharge hole 45b).

Thus, as the rotor 50 rotates, 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 sucked from the suction chamber 13 is increased to the first pressure. The ink is discharged from the discharge hole 45a (and the second discharge hole 45b).

In addition, a discharge valve 61 and a valve support 62 are installed around the second discharge hole 45b. The discharge valve 61 is elastically deformed so as to warp toward the discharge chamber 46b when the pressure of the refrigerant gas in the compression chamber 43 (the compression chamber 43b in FIG. 2) in the compression stroke becomes equal to or higher than a predetermined discharge pressure. When the refrigerant gas pressure does not reach the predetermined discharge pressure, the second discharge hole 45b is closed by an elastic force. The valve support 62 prevents the discharge valve 61 from excessively warping toward the discharge chamber 46b. The first discharge hole 45a is not provided with these discharge valves and valve supports, and is always open.

The oil separator 70 separates the refrigeration oil mixed with the refrigerant gas (the vane back pressure oil leaked from the vane groove 59 formed in the rotor 50 into the cylinder chamber 42 (compression chamber 43)) from the refrigerant gas. The high-pressure refrigerant gas discharged from the first and second discharge holes 45a and 45b and introduced through the

discharge chambers

46a and 46b and the

discharge passages

30a and 30b is spirally swirled to refrigerating machine oil. It is configured to centrifuge.

The refrigerating machine oil R (see FIG. 1) separated from the refrigerant gas is accumulated at the bottom of the discharge chamber 14, and the high-pressure refrigerant gas G2 after the refrigerating machine oil R is separated passes through the discharge port 11a from the top of the discharge chamber 14. And discharged to a condenser (not shown).

The refrigerating machine oil R stored in the bottom of the discharge chamber 14 is passed through the oil passage 38a formed in the rear side block 30 and the

Sarai grooves

31 and 32, which are recesses for supplying back pressure, by the high pressure atmosphere in the discharge chamber 14, and the rear side. These are

oil passages

38 a and 38 b formed in the block 30, an oil passage 44 formed in the cylinder 40, an oil passage 24 formed in the front side block 20, and a back pressure supply recess formed in the front side block 20. It is supplied to the vane groove 59 of the rotor 50 through the

Sarai grooves

21 and 22, respectively, and becomes a back pressure that causes the vane 58 to protrude outward.

The refrigerating machine oil oozes out from the gap between the vane 58 and the vane groove 59, the gap between the rotor 50 and each side block 20, 30, and the like. And the lubricating and cooling functions at the contact portion between the vane 58 and the contact portion between the vane 58 and the cylinder 40 or each of the side blocks 20 and 30, etc., and a part of the refrigerating machine oil is refrigerant gas in the compression chamber 43. Therefore, refrigerating machine oil is separated by the oil separation unit 70.

Of the two

Sarai grooves

31 and 32 formed in the rear side block 30, a portion downstream of the rotor 50 in the rotational direction with respect to the proximity portion 48 of the cylinder chamber 42 (a portion corresponding to the suction stroke and the compression stroke) is formed. The refrigerating machine oil supplied to the Saray groove 31 is supplied to the Saray groove 31 from the oil passage 38 a through a narrow gap between the bearing 37 and the outer peripheral surface of the rotary shaft 51. For this reason, the medium pressure (suction chamber) lower than the high pressure (pressure close to the discharge pressure) that is the atmosphere of the discharge chamber 14 due to the pressure loss when passing through the narrow gap between the bearing 37 and the outer peripheral surface of the rotary shaft 51. 13 is a pressure higher than the suction pressure).

Of the two

salai grooves

21 and 22 formed in the front side block 20, the refrigerating machine oil supplied to the salai groove 21 formed in the downstream portion in the rotation direction of the rotor 50 with respect to the proximity portion 48 of the cylinder chamber 42. As for the refrigeration oil supplied to the saray groove 31 as well, it becomes an intermediate pressure.

On the other hand, of the two

Sarai grooves

31 and 32 formed in the rear side block 30, it is formed in a portion upstream of the rotor 50 in the rotation direction with respect to the proximity portion 48 of the cylinder chamber 42 (mainly corresponding to the discharge stroke). Since the refrigerating machine oil supplied to the saray groove 32 is supplied without pressure loss from the oil passage 38a, it becomes a pressure close to a high pressure (pressure higher than the medium pressure) that is the atmosphere of the discharge chamber 14.

Of the two

salai grooves

21, 22 formed in the front side block 20, the salai grooves 22 are formed in the upstream portion of the rotor 50 in the rotation direction with respect to the proximity portion 48 of the cylinder chamber 42. The refrigerating machine oil also has a high pressure similarly to the refrigerating machine oil supplied to the saray groove 32.

Then, when the vane groove 59 penetrating to both end faces of the rotor 50 communicates with the

Sarai grooves

21, 31, 22, 32 of the side blocks 20, 30 due to the rotation of the rotor 50, the connected Saray grooves 21. , 31, 22, 32 are supplied with the refrigeration oil to the vane groove 59, and the pressure of the supplied refrigeration oil becomes a back pressure that causes the vane 58 to protrude.

(Detailed configuration of the first and second discharge holes 45a and 45b)
Next, the first and second discharge holes 45a and 45b formed in the inner circumferential surface 40a of the cylinder 40 along the circumferential direction will be described in detail with reference to FIG.

First, the first discharge hole 45a formed on the upstream side immediately before the proximity portion 48 along the rotation direction W of the rotor 50 allows only one cycle of suction, compression, and discharge during one rotation of the rotor 50. This corresponds to the original single discharge hole in the gas compressor having a configuration including only a single discharge hole, and can be called a main discharge hole. On the other hand, the second discharge hole 45b formed so as to be positioned upstream of the first discharge hole 45a along the rotation direction W of the rotor 50 can be referred to as a sub discharge hole.

As the rotor 50 rotates, the pressure of the refrigerant gas in the compression chamber 43a facing the first discharge hole 45a becomes higher than a predetermined pressure (predetermined discharge pressure), and the high-pressure refrigerant gas G2 is It is configured to be discharged from one discharge hole 45a. The high-pressure refrigerant gas G2 discharged from the first discharge hole 45a is introduced into the discharge chamber 14 through the oil separation portion 70 via the discharge chamber 46a and the discharge path 30a.

The compression chamber 43b adjacent to the compression chamber 43a on the upstream side of the compression chamber 43a along the rotation direction W of the rotor 50 is the volume of the compression chamber 43a when the compression chamber 43a faces the first discharge hole 45a. The pressure of the refrigerant gas compressed in the compression chamber 43b reaches the predetermined pressure (predetermined discharge pressure) before the compression chamber 43b rotates to the position facing the first discharge hole 45a. It can happen.

In such a case, in a gas compressor in which only one discharge hole (only the first discharge hole 45a) is formed, the volume of the compression chamber 43b is further reduced with the rotation of the rotor 50, so that the compression chamber The pressure of the refrigerant gas in 43b exceeds a predetermined pressure (predetermined discharge pressure), but exceeded the predetermined pressure (predetermined discharge pressure) before the compression chamber 43b rotates to the position facing the first discharge hole 45a. The refrigerant gas is not discharged.

At this time, of the two vanes (in FIG. 2,

vanes

58a and 58b) partitioning the compression chamber 43b, the back pressure from the vane groove 59 by the refrigerating machine oil and the vane 58b A pressing force is applied to the inner peripheral surface 40a of the cylinder 40 due to the resultant force with the centrifugal force acting on the cylinder 40. And if the force which pushes back the front end side of the vane 58b from the internal peripheral surface 40a of the cylinder 40 by the internal pressure of the compression chamber 43b exceeds, the protrusion side front-end | tip part of the vane 58b will leave | separate from the internal peripheral surface 40a of the cylinder 40. Thereafter, when the refrigerant gas in the compression chamber 43b is discharged from the discharge hole (first discharge hole 45a), the vane 58b collides with the inner peripheral surface 40a of the cylinder 40.

In this way, noise (hereinafter referred to as “chattering”) is generated when the vane 58 (in FIG. 2, the vane 58 b in FIG. 2) repeats the separation and the collision with the inner peripheral surface 40 a of the cylinder 40 during the operation of the compressor 100. .

On the other hand, the compressor 100 of the present embodiment described above is when the pressure of the refrigerant gas in the compression chamber 43b reaches a predetermined pressure (predetermined discharge pressure) at a stage before facing the first discharge hole 45a. The second discharge hole 45b for discharging the high-pressure refrigerant gas G2 in the compression chamber 43b is provided upstream of the first discharge hole 45a in the rotor rotation direction.

For this reason, even if the pressure of the refrigerant gas in the compression chamber 43b reaches a predetermined pressure (predetermined discharge pressure) before reaching the first discharge hole 45a, the high pressure in the compression chamber 43b is reached. The refrigerant gas G2 is introduced into the discharge chamber 14 from the second discharge hole 45b through the oil separation portion 70 via the discharge chamber 46b and the discharge path 30b. At this time, the discharge valve 61 is elastically deformed and opened by the high-pressure refrigerant gas G2 discharged from the second discharge hole 45b.

As described above, the two first discharge holes 45a and the second discharge holes 45b are formed along the circumferential direction on the inner peripheral surface 40a of the cylinder 40, whereby the pressure of the refrigerant gas in the compression chamber 43b is increased. Even when the predetermined pressure (predetermined discharge pressure) is reached in the stage before facing the first discharge hole 45a, the refrigerant gas in the compression chamber 43b can be discharged from the second discharge hole 45b. Therefore, it is possible to prevent overcompression in which the pressure of the refrigerant gas in the compression chamber 43b exceeds a predetermined pressure (predetermined discharge pressure).

This can reduce power loss during operation of the compressor 100. Further, the protrusion-side tip of the vane 58 (vane 58b in FIG. 2) does not repeat separation and collision with the inner peripheral surface 40a of the cylinder 40, and chattering can be prevented.

Incidentally, as described above, the discharge valve 61 and the valve support 62 are provided on the discharge side of the second discharge hole 45b, and the pressure of the refrigerant gas in the compression chamber 43b faces the first discharge hole 45a. When a predetermined pressure (predetermined discharge pressure) is reached in the previous stage, the discharge valve 61 is opened and high-pressure refrigerant gas is discharged from the second discharge hole 45b.

That is, the discharge valve 61 of the second discharge hole 45b is closed when the pressure of the refrigerant gas in the compression chamber 43b has not reached the predetermined pressure (predetermined discharge pressure), and closes the second discharge hole 45b. It is out. This is because when the pressure of the refrigerant gas in the compression chamber 43b does not reach the predetermined pressure (predetermined discharge pressure), the high-pressure refrigerant gas flows backward from the discharge chamber 14 (discharge chamber 46b) side to the compression chamber 43b side. This is to prevent this.

On the other hand, the first discharge hole 45a is not provided with a discharge valve and a valve support provided on the second discharge hole 45b side, and is always open.

This is because during operation of the compressor 100, the refrigerant gas compressed in the compression chamber 43a (the compression chamber having the first discharge hole 45a) always reaches a predetermined pressure (predetermined discharge pressure) and is in a discharge state. Therefore, even if no discharge valve is provided in the first discharge hole 45a, the high-pressure refrigerant gas does not flow backward from the discharge chamber 14 (discharge chamber 46a) side to the compression chamber 43a side.

As described above, since the discharge valve and the valve support on the first discharge hole 45a side can be eliminated, the number of parts of the discharge valve and the valve support can be reduced, thereby reducing the cost. Can be achieved.

In the case of a configuration in which a discharge valve is provided on the first discharge hole 45a side, the refrigerant gas compressed in the compression chamber 43a always reaches a predetermined pressure (predetermined discharge pressure). The valve opens. However, since the volume of the compression chamber 43a is small, the discharge amount of the refrigerant gas from the first discharge hole 45a is small. Therefore, immediately after the vane 58 passes through the first discharge hole 45a, the discharge valve instantaneously The operation of closing and immediately opening the discharge valve may be repeated.

For this reason, when this discharge valve opens and closes and hits the periphery of the first discharge hole 45a, a collision sound (noise) may be generated. In the present invention, the discharge valve is formed around the first discharge hole 45a. Therefore, such a collision noise (noise) of the discharge valve does not occur.

<Embodiment 2>
FIG. 3 is a cross-sectional view of a compressor (vane rotary type gas compressor) according to Embodiment 2 of the present invention. In addition, the same code | symbol is attached | subjected to the member which has the same function as the compressor of the said Embodiment 1 shown in FIG. 1, FIG. 2, and the overlapping description is abbreviate | omitted.

In the first embodiment, the five vanes 58 are slidably fitted in the vane grooves 59 of the rotor 50 at equal angular intervals. However, in this embodiment, as shown in FIG. A plurality of

vanes

58a, 58b, and 58c are slidably fitted into the vane grooves 59 of the rotor 50 at equal angular intervals, and a plurality of compression chambers 43 partitioned by the

vanes

58a, 58b, and 58c are formed in the cylinder chamber 42. ing.

Furthermore, in the first embodiment, the first discharge hole 45a is not provided with a discharge valve, and the second discharge hole 45b is provided with a discharge valve 61. In the present embodiment, FIG. As shown, both the first and second discharge holes 45a and 45b have a configuration in which neither a discharge valve nor a valve support is provided. Other configurations are substantially the same as those of the first embodiment.

In the present embodiment, as shown in FIG. 3, the compression chamber 43b formed by the two front vanes 58a and the rear vane 58b facing the second discharge hole 45b is as in the first embodiment. Compared with the case where there are five vanes, the interval between the vanes along the circumferential direction becomes longer, and the compression process becomes longer. Therefore, as the rotor 50 rotates, the volume of the compression chamber 43b becomes smaller, so that the refrigerant gas is further compressed and substantially reaches a predetermined discharge pressure near the second discharge hole 45b.

In FIG. 3, the front vane 58a moves to the downstream side of the second discharge hole 45b along the rotation direction of the rotor 50, but the refrigerant gas compressed in the compression chamber 43b is the predetermined discharge pressure. When the pressure reaches approximately, the front vane 58a is just before reaching the second discharge hole 45b. Therefore, immediately after the vane 58a passes through the second discharge hole 45b, the refrigerant gas G2 in the compression chamber 43b that has substantially reached the predetermined discharge pressure is discharged from the second discharge hole 45b.

In this embodiment, in FIG. 3, the discharge is such that the compression ratio in the compression chamber 43b is 4 to 6 with respect to the suction pressure of the refrigerant gas G1 sucked into the compression chamber 43 through the suction hole 23. The position of the second discharge hole 45b is set so that the front vane 58a reaches the second discharge hole 45b at the timing when the pressure is reached.

The high-pressure refrigerant gas G2 discharged from the second discharge hole 45b is introduced into the oil separation unit 70 and the discharge chamber 14 (see FIG. 1) through the discharge chamber 46b and the discharge path 30b.

Further, a part of the high-pressure refrigerant gas (hereinafter referred to as “residual gas”) remaining in the compression chamber 43 b without being discharged from the second discharge hole 45 b is generated by the front vane 58 a as the rotor 50 rotates. After passing through the second discharge hole 45b, it is discharged from the first discharge hole 45a facing the compression chamber 43a. The residual gas G2 'discharged from the first discharge hole 45a is introduced into the oil separation unit 70 and the discharge chamber 14 through the discharge path 30a. Therefore, in the present embodiment, the second discharge hole 45b is a main discharge hole and the first discharge hole 45a is a sub discharge hole, contrary to the case of the first embodiment.

Thus, in the present embodiment, the refrigerant gas in the compression chamber 43b can be discharged from the second discharge hole 45b when the pressure of the refrigerant gas in the compression chamber 43b substantially reaches a predetermined discharge pressure. Can be prevented from exceeding the predetermined pressure (predetermined discharge pressure).

Further, in the present embodiment, during the operation of the compressor, the first and second discharge holes 45a and 45b are caused to discharge the refrigerant gas that has substantially reached a predetermined discharge pressure, whereby the first and second discharge holes are discharged. Both of the

holes

45a and 45b do not require a discharge valve and a valve support for preventing the backflow of the refrigerant gas. As described above, since no discharge valve is provided in each of the first and second discharge holes 45a and 45b, a collision sound (noise) due to opening and closing of the discharge valve does not occur.

<Embodiment 3>
FIG. 4 is a cross-sectional view of a compressor (vane rotary type gas compressor) according to Embodiment 3 of the present invention. In addition, the same code | symbol is attached | subjected to the member which has the same function as the compressor of the said Embodiment 1 shown in FIG. 1, FIG. 2 and the said Embodiment 2 shown in FIG. 3, and the overlapping description is abbreviate | omitted.

In the present embodiment, the three

vanes

58a, 58b, and 58c shown in the second embodiment are provided, and neither the first or second discharge holes 45a and 45b are provided with a discharge valve or a valve support. In this compressor, as shown in FIG. 4, a third discharge hole 45c is formed in the inner peripheral surface 40a of the cylinder 40 located on the upstream side in the rotor rotation direction with respect to the second discharge hole 45b.

The third discharge hole 45c is provided at a position facing the vicinity of the intermediate position between the first and second discharge holes 45a and 45b with the rotation shaft 51 therebetween. A discharge valve 61a and a valve support 62a are installed around the third discharge hole 45c. The third discharge hole 45c communicates with the oil separation unit 70 and the discharge chamber 14 (see FIG. 1) through the discharge chamber 46c and the discharge path 30c. The discharge passage 30c communicates with the

discharge passages

30a and 30b. The discharge valve 61a and the valve support 62a are provided in the discharge chamber 46c. Other configurations are the same as those of the second embodiment.

In the present embodiment, as shown in FIG. 4, the pressure of the refrigerant gas in the compression chamber 43c formed by the two vanes 58b and the vanes 58c is a predetermined pressure before reaching the second discharge hole 45b. Even in this case, the high-pressure refrigerant gas in the compression chamber 43c is introduced into the discharge chamber 14 from the third discharge hole 45c through the oil separation portion 70 via the discharge chamber 46c and the discharge path 30c. At this time, the discharge valve 61a is elastically deformed by the high-pressure refrigerant gas discharged from the third discharge hole 45c and opens.

As described above, in this embodiment, in addition to the effects obtained in the second embodiment, the pressure of the refrigerant gas in the compression chamber 43c reaches a predetermined pressure before reaching the second discharge hole 45b. Even if it exists, since the refrigerant gas in the compression chamber 43c can be discharged from the 3rd discharge hole 45c, the overcompression in which the pressure of the refrigerant gas in the compression chamber 43c exceeds predetermined pressure can be prevented.

Cross-reference of related applications

This application claims priority based on Japanese Patent Application No. 2012-127731 filed with the Japan Patent Office on June 5, 2012 and Japanese Patent Application No. 2013-114737 filed with the Japan Patent Office on May 31, 2013 The entire disclosure of which is hereby incorporated by reference in its entirety.

DESCRIPTION OF SYMBOLS 10 Housing 13 Suction chamber 14 Discharge chamber 20 Front side block 30 Rear side block 40 Cylinder 42

Cylinder chamber

43, 43a, 43b, 43c Compression chamber 45a 1st discharge hole 45b 2nd discharge hole 45c 3rd discharge hole 50 Rotor 51 Rotating

shaft

58, 50a, 50b, 50c Vane 60

Compressor body

61,

61a Discharge valve

62, 62a Valve support 70 Oil separation unit 100 Compressor (gas compressor)

Claims

A substantially cylindrical rotor that rotates integrally with the rotating shaft;
A cylinder having an inner peripheral surface with a contour shape surrounding the rotor from the outside of the outer peripheral surface of the rotor;
A plurality of plate-like vanes provided in a vane groove formed in the rotor so as to protrude from the outer peripheral surface of the rotor toward the inner peripheral surface of the cylinder;
Two side blocks respectively closing both ends of the rotor and the cylinder,
The vane forms a plurality of compression chambers by partitioning a space formed between an inner peripheral surface of the cylinder and an outer peripheral surface of the rotor, and each of the formed compression chambers is formed in the rotor. A gas compressor in which the contour shape of the inner peripheral surface of the cylinder is set so that the medium is sucked, compressed, and discharged in only one cycle during one rotation period,
The medium compressed in the compression chamber on the upstream side in the rotation direction of the rotor with respect to a region where the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor are closest to each other in a range of one circumference around the axis of the rotation shaft. Having at least two discharge holes for discharging to the outside along the circumferential direction of the inner peripheral surface of the cylinder;
Among the discharge holes, at least the first discharge hole on the side closest to the closest region opens when the pressure of the medium compressed in the compression chamber reaches a predetermined discharge pressure, The gas compressor is characterized in that no discharge valve is provided to close the valve when the predetermined discharge pressure is not reached, and communicates with the outside.
The pressure of the medium compressed in the compression chamber facing the second discharge hole is equal to the predetermined discharge pressure in the second discharge hole located upstream of the first discharge hole in the rotation direction of the rotor. The gas compressor according to claim 1, further comprising a discharge valve that opens when the pressure reaches the valve and closes when the predetermined discharge pressure is not reached.
The first discharge hole constantly discharges the medium in the compression chamber facing the first discharge hole, which has reached the predetermined discharge pressure during compressor operation. Item 3. The gas compressor according to Item 1 or 2.
The pressure of the medium compressed in the compression chamber facing the second discharge hole is also set to the predetermined discharge pressure in the second discharge hole located upstream of the first discharge hole in the rotation direction of the rotor. 2. The gas compressor according to claim 1, wherein the gas compressor is not provided with a discharge valve that opens when the pressure reaches, and closes when the predetermined discharge pressure is not reached, and communicates with the outside. .
When the medium compressed in the compression chamber partitioned by two adjacent vanes substantially reaches the predetermined discharge pressure, the front vane of the two vanes passes through the second discharge hole. The gas compressor according to claim 4, wherein the medium in the compression chamber that has reached the predetermined discharge pressure is discharged to the outside from the second discharge hole.
A part of the residual medium remaining in the compression chamber without being discharged from the second discharge hole is discharged to the outside from the first discharge hole after the front vane passes through the first discharge hole. The gas compressor according to claim 5.