KR102058799B1 - Vane compressor - Google Patents

Abstract

(Problem) Provided is a vane compressor capable of sucking an appropriate amount of refrigerant into a compression chamber in response to a suction stroke.
(Solution means) The suction windows 23a and 27a in which the suction passages for sucking the refrigerant into the compression chamber open in the inner circumferential surface 14c of the cylinder portion 14 start the opening with respect to the rotational direction R of the rotor. It has the start end part 23c, 27c and the end part 23d, 27d which complete | opens an opening, is extended, and is the end part 23d, 27d including the end part 23d, 27d, and the end part 23d, 27d. ) And axial widths W2 and W4 longer than the predetermined widths W1 and W3 of the starting end portion between the end portions 23c and 27c.

Description

Vane Compressor {VANE COMPRESSOR}

The present invention relates to a vane compressor.

Related to a conventional vane type compressor, Japanese Laid-Open Patent Publication No. 58-173795 (Patent Document 1) discloses that refrigerant is sucked into a cylinder from the intake ports of both end faces of the cylinder, Disclosed is a configuration that is compressed by volume variation and discharged from a discharge port.

Japanese Utility Model Publication No. 58-173795

In the vane compressor, a compression chamber is defined between the rotating rotor and the cylinder. At the start of suction of the refrigerant into the compression chamber, the gap between the rotor and the cylinder is small and the volume of the compression chamber is small. As the rotor rotates, the volume of the compression chamber gradually increases.

In the vane type compressor described in the above document, the width in the rotational axis direction of the opening of the intake port on the inner circumferential surface of the cylinder is constant in the rotational direction, and the opening area increases at a constant rate with rotation. Even if the volume of the compression chamber changes abruptly, the rate of increase of the opening area does not change, which is a restriction on changing the suction amount of the refrigerant into the compression chamber.

An object of the present invention is to provide a vane type compressor which allows suction of an appropriate amount of refrigerant into a compression chamber in response to a suction stroke.

In order to achieve the above object, the vane-type compressor of the present invention includes a cylindrical cylinder portion having an inner circumferential surface, a partition wall partitioning the cylinder chamber inside the cylinder portion, a rotating shaft rotatably formed in the cylinder chamber, and a rotating shaft. A rotor connected to the outer periphery of the plurality of vane grooves, a vane mounted to each of the plurality of vane grooves, and a compression chamber partitioned by partition walls, rotors, and vanes in the cylinder chamber, and a compression chamber. A suction passage for sucking the refrigerant is provided. The suction passage is provided with a suction window opened in the inner circumferential surface of the cylinder portion. The suction window extends with respect to the rotational direction of the rotor, with a start end beginning the opening and a terminal end ending the opening. The start end is a width of a predetermined length in the axial direction of the rotor. It is assumed that the terminal portion has an axial width longer than the predetermined width between the terminal portion and the start portion, including the terminal portion.

According to this structure, in the latter half of the suction stroke in which the compression chamber is large, the refrigerant can be sucked into the compression chamber via the suction window in which the width in the rotation axis direction of the suction window increases and the opening area is increased. By changing the suction amount of the refrigerant in response to the volume change of the compression chamber, an appropriate amount of refrigerant can be sucked into the compression chamber in response to the suction stroke.

In the vane compressor described above, the suction window may have a long axial width at the end portion side by the step portion. According to such a structure, the axial width of the suction window on the terminal side side can be reliably longer than the axial width of the suction window on the start end side than the step portion.

Said vane type | mold compressor is provided with the suction port which communicates with a suction path, and suctions refrigerant from the outside, and a suction window may be inflated toward the direction falling from a suction port in the terminal part side. Alternatively, the suction window may be formed in a pair apart from the rotor in the axial direction, and the opening area of the suction window on the side farther from the suction port may be larger among the pair of suction windows. According to such a structure, in the side which falls away from the suction port in the axial direction of a rotor, the axial width of a suction window becomes larger than the side near a suction port. Uniformity of the flow rate of the refrigerant flowing into the compression chamber is improved on the side close to the suction port in the axial direction and on the side away from the suction port. As a result, the refrigerant can be sucked into the compression chamber more efficiently, and the pulsation of the density of the refrigerant sucked into the compression chamber can be suppressed.

In the vane-type compressor, the suction window may gradually increase in the axial width from the start end side in the rotational direction toward the end end side. According to such a structure, the suction amount of the refrigerant | coolant to a compression chamber can be adjusted more appropriately according to the volume change of a compression chamber.

In the vane compressor described above, the length of the suction window in the circumferential direction of the rotary shaft may be smaller than the distance between neighboring vane grooves in the circumferential direction of the rotary shaft. According to this structure, a refrigerant | coolant can be suctioned in a compression chamber reliably.

According to the vane compressor of the present invention, an appropriate amount of refrigerant can be sucked into the compression chamber in response to the suction stroke.

1 is a cross-sectional view showing a compressor according to the first embodiment.
FIG. 2 is a cross-sectional view of the compressor along the II-II line shown in FIG. 1. FIG.
FIG. 3 is a cross-sectional view of the compressor along the III-III line shown in FIG. 1. FIG.
4 is a cross-sectional view of the compressor along the IV-IV line shown in FIG. 1.
5 is a cross-sectional view of the compressor along the VV line shown in FIG. 1.
FIG. 6: is sectional drawing of the cylinder part along the VI-VI line shown to FIGS. 2-5.
7 is a graph showing the relationship between the rotational phase and the compression chamber volume.
8 is a cross-sectional view of the cylinder portion according to the second embodiment.
9 is a sectional view of a cylinder portion according to the third embodiment.
10 is a sectional view of a cylinder portion according to the fourth embodiment.
11 is a sectional view of a cylinder portion according to the fifth embodiment.

EMBODIMENT OF THE INVENTION Hereinafter, the compressor which concerns on each embodiment is demonstrated with reference to drawings. In the following description, the same code | symbol is attached | subjected to the same or equivalent part in drawing, and the description is not repeated. In addition, the arrangement | positioning of each structure of a compressor is shown and changed suitably in each figure for convenience of description.

(Embodiment 1)

[Configuration of Compressor 10]

1 is a cross-sectional view showing the compressor 10 according to the first embodiment. FIG. 2 is a cross-sectional view of the compressor 10 along the II-II line in FIG. 1. 3 is a cross-sectional view of the compressor 10 along the line III-III in FIG. 1. 4 is a cross-sectional view of the compressor 10 along the IV-IV line in FIG. 1. FIG. 5 is a cross-sectional view of the compressor 10 along the V-V line in FIG. 1. The compressor 10 is a vane type compressor. The compressor 10 is mounted on a vehicle and used for an air conditioner of the vehicle.

In the following description, the left direction is called front in the figure of the compressor 10 shown in FIG. 1, and the right direction is called back in the figure of the compressor 10 shown in FIG. The axial direction, radial direction, and circumferential direction in the following description have shown the axial direction, the radial direction, and the circumferential direction of the rotating shaft 16 and the rotor 18 which are rotating bodies.

As shown in FIG. 1, the housing 11 of the compressor 10 has a front coupled to a bottomed cylindrical rear housing 12 (shell) and a front end face of the rear housing 12. It is formed of the housing 13. The rear housing 12 has a circumferential wall 12a (see FIGS. 2 to 5). The front housing 13 has a cylindrical cylinder part 14 and the bottom wall part 13a which closes the internal space of the cylinder part 14. The front housing 13 is formed in the cylindrical shape with a bottom. The cylinder portion 14 is housed in the rear housing 12. The bottom wall part 13a and the cylinder part 14 are integrally formed. The material of the rear housing 12 and the front housing 13 is metal, for example.

The cylinder part 14 has the open end part 14e which is an open end part on the opposite side to the bottom wall part 13a. The rear side plate 15 is disposed opposite the open end 14e of the cylinder portion 14. The rear side plate 15 is fixed to the open end 14e of the cylinder portion 14 using a bolt (not shown). The front housing 13 and the rear side plate 15 rotatably support the rotation shaft 16. The rotating shaft 16 has penetrated the inside of the cylinder part 14. Between the rotating shaft 16 and the front housing 13, the shaft rod device 17a which prevents the leakage of the refrigerant gas along the peripheral surface of the rotating shaft 16 is formed.

The cylinder chamber 14d is partitioned by the cylindrical cylinder portion 14, the bottom wall portion 13a and the rear side plate 15. In the cylinder chamber 14d, a rotor 18 having a cylindrical shape is formed. The rotor 18 is attached to the rotating shaft 16 so that rotation is possible. The front end face of the rotor 18 opposes the rear face 13s of the bottom wall portion 13a. The rear end face of the rotor 18 opposes the front face 15s of the rear side plate 15.

As shown in FIGS. 2-5, the inner peripheral surface 14c of the cylinder part 14 is formed in elliptical shape. In the cylinder chamber 14d, the rotor 18 is rotatably formed. On the outer circumferential surface of the rotor 18, a plurality of vane grooves 18a are formed to extend radially. In each of the plurality of vane grooves 18a, the vanes 19 are housed so that they can be sunk. Each of the plurality of vane grooves 18a is supplied with lubricating oil in the discharge region 35 described later.

The outer circumferential surface of the rotor 18, the inner circumferential surface 14c of the cylinder portion 14, two vanes 19 neighboring in the circumferential direction, the rear face 13s of the bottom wall portion 13a, and the rear side plate The compression chamber 21 is partitioned by the front face 15s of 15. As shown in FIGS. 2-5, in this embodiment, the some compression chamber 21 is formed in 14d of cylinder chambers.

As shown in FIGS. 1-3, the suction port 22 which penetrates the circumferential wall 12a is formed in the rear housing 12. As shown in FIG. The joint part 24 is connected to the outer peripheral part of the suction port 22. The joint 24 is connected to a suction pipe 25 extending toward the outside of the compressor 10 (for example, an evaporator of an external refrigerant circuit). In the suction port 22, a non-shown check valve is formed to prevent the back flow of the refrigerant.

The recessed part 14a is formed in the outer peripheral surface of the cylinder part 14 over the perimeter of the cylinder part 14 in the circumferential direction. The suction space 20 is partitioned by the inner peripheral surface of the recess 14a and the rear housing 12. The suction space 20 is formed between the cylinder part 14 and the rear housing 12 in the radial direction of the rotating shaft 16. The suction space 20 communicates with the suction port 22.

As shown to FIG. 2, 3, the suction space 20 is formed annularly between the cylinder part 14 and the rear housing 12, and is extended in the circumferential direction.

The cylinder portion 14 communicates with a pair of suction holes 23 (FIGS. 2 and 3), a pair of suction holes 27, and suction holes 23 and 27 communicating with the suction space 20. The communication path 26 is formed.

The suction hole 23 penetrates the cylinder portion 14 in the radial direction and opens in the suction space 20, and opens in the inner circumferential surface 14c of the cylinder portion 14. The suction hole 23 is formed in the front end portion of the cylinder portion 14 which is connected to the rear surface 13s of the bottom wall portion 13a. The suction hole 23 is partitioned off by the rear face 13s of the bottom wall portion 13a.

The suction hole 23 has a suction window 23a that opens in the inner circumferential surface 14c of the cylinder portion 14. The suction window 23a is opened in the compression chamber 21.

The suction hole 23, the suction space 20, and the suction port 22 are formed radially outward with respect to the compression chamber 21. The suction hole 23, the suction space 20, and the suction port 22 are the rear face 13s of the bottom wall portion 13a and the front face of the rear side plate 15 in the axial direction of the rotation shaft 16. It exists in the area between 15s. The suction space 20 and the suction port 22 are formed in the front side of the compression chamber 21 in the axial direction of the rotating shaft 16.

The cylinder portion 14 is further provided with a pair of communication paths 26 communicating with the suction space 20 and a pair of suction holes 27 communicating with each communication path 26 (FIG. 4, 5).

The communication path 26 extends in the cylinder portion 14 in the axial direction and opens in the suction space 20. The suction hole 23 and the suction hole 27 communicate with each other via the communication path 26.

The suction hole 27 extends in the radial direction and penetrates the cylinder part 14 in the radial direction. The suction hole 27 is open to the communication path 26 and is open to the open end 14e and the inner circumferential surface 14c of the cylinder portion 14. The suction hole 27 forms a notch in the open end 14e of the cylinder part 14, and is formed by blocking the rear side of the notch by opposing the front face 15s of the rear side plate 15 to this notch. It is. The suction hole 27 is partitioned by the cutout and the rear side plate 15 formed in the open end 14e of the cylinder portion 14.

The suction hole 27 has a suction window 27a that opens in the inner circumferential surface 14c of the cylinder portion 14. The suction window 27a is opened in the compression chamber 21.

The communication path 26 and the suction hole 27 are formed in the radially outer side with respect to the compression chamber 21.

As shown to FIG. 4, 5, the pair of recessed part 14b is formed in the outer peripheral surface of the cylinder part 14 (refer FIG. 1). The pair of recesses 14b are located on opposite sides with the rotation shaft 16 interposed therebetween. Each recessed part 14b intersects with the extension formation surface 141b extended from the outer peripheral surface of the cylinder part 14 toward the rotating shaft 16, and the extension formation surface 141b, and the outer peripheral surface of the cylinder part 14 It is formed with the mounting surface 142b extended toward the surface.

A pair of discharge chamber 30 is partitioned by the extended formation surface 141b, the mounting surface 142b, and the inner peripheral surface of the rear housing 12. As shown in FIG. The discharge chamber 30 is located between the cylinder portion 14 and the rear housing 12 in the radial direction (see FIG. 1). The cylinder part 14 is formed with the discharge port 31 which opens in the mounting surface 142b, and communicates the compression chamber 21 and the discharge chamber 30 with each other. The discharge port 31 is opened and closed by the discharge valve 32 attached to the mounting surface 142b. The refrigerant gas compressed in the compression chamber 21 pushes out the discharge valve 32 and is discharged to the discharge chamber 30 via the discharge port 31.

The discharge chamber 30 is located closer to the rear side plate 15 than the suction space 20.

4 and 5, the discharge port 31 is formed at a position away from the open end 14e of the cylinder portion 14. In the end surface of the vicinity of the open end 14e of the cylinder part 14 shown in FIG. 5, the discharge port 31 is not shown. On the other hand, in the cross section away from the open end 14e of the cylinder part 14 shown in FIG. 4, the discharge port 31 is shown.

As shown in FIG. 1, the discharge port 34 is formed in the circumferential wall 12a of the rear housing 12. As shown in FIG. The joint portion 38 is formed in the discharge port 34. The joint 38 is connected to a discharge pipe 39 extending toward the outside of the compressor 10 (for example, a capacitor of an external refrigerant circuit).

On the rear side of the rear housing 12, the discharge region 35 is partitioned by the rear side plate 15. In the discharge area 35, an oil separator 36 is disposed. The oil separator 36 is formed to separate lubricant oil contained in the refrigerant gas. The oil separator 36 has a bottomed cylindrical case 36a. The cylindrical oil separation cylinder 36b is fitted and fixed to the opening side of the case 36a.

The oil passage 36c is formed in the lower part of the case 36a. The oil passage 36c communicates with the case 36a and the bottom side of the discharge region 35. Discharge passages 37 are formed in the rear side plate 15 and the case 36a (see FIGS. 4 and 5). The discharge passage 37 communicates with the discharge chamber 30 and the inside of the case 36a. An oil supply passage 15d is formed in the rear side plate 15. The oil supply passage 15d guides the lubricating oil stored in the bottom side of the discharge region 35 to the vane groove 18a.

FIG. 6: is sectional drawing of the cylinder part 14 along the VI-VI line shown to FIGS. 6, the cross section of a part of the cylinder part 14 and the bottom wall part 13a along the long diameter of the ellipse which the inner peripheral surface 14c of the cylinder part 14 makes is shown. The left-right direction in FIG. 6 is an axial direction of the rotating shaft 16 and the rotor 18. The rotation direction R shown by the arrow in FIG. 6 is a rotation direction of the rotating shaft 16 and the rotor 18, as shown also in FIGS. The lower side in FIG. 6 is a leading side in the rotation direction R, and the upper side in FIG. 6 is a trailing side in the rotating direction R. FIG. In addition, the leading side of rotation direction R refers to the side which communicates with a suction window previously, and the trailing side of rotation direction R refers to the side which communicates with a suction window from behind.

The suction hole 23 and the suction hole 27 are formed along the axial direction. The suction hole 23 is formed in the position which continues to the rear surface 13s of the bottom wall part 13a in the axial direction, and is formed in front of the suction hole 27. The suction hole 27 is formed in the position which continues to the open edge part 14e of the cylinder part 14 in the axial direction, and is formed in the back with respect to the suction hole 23. The discharge port 31 is formed at a position away from the rear face 13s of the bottom wall portion 13a and spaced apart from the open end 14e of the cylinder portion 14.

As shown to FIG. 6, FIG. 2, 3, the suction window 23a which the suction hole 23 opens to the inner peripheral surface 14c of the cylinder part 14 starts an opening with respect to the rotation direction R. As shown to FIG. It extends with the start end 23c and the end 23d which complete | opens an opening. The start end portion 23c has a width of a predetermined length in the axial direction. As for the suction window 23a, the axial direction width of the rotating shaft 16 is formed in the terminal part 23d side rather than the start end part 23c side. The axial direction width W2 of the terminal part 23d shown in FIG. 6 is larger than the axial direction width W1 of the start end part 23c. The suction window 23a of this embodiment has the step part 23b in which the axial width of the rotating shaft 16 becomes large rapidly. The axial width of the suction window 23a is relatively smaller on the starting end 23c side than the stepped portion 23b, and the axial width of the suction window 23a is relatively on the end 23d side than the stepped portion 23b. Big. The suction window 23a is larger than the start end 23c side with respect to the stepped portion 23b at the end 23d side with respect to the step 23b.

The suction window 23a opens larger in the terminal portion 23d than the start end portion 23c. When the length of the rotational direction R of the suction window 23a is divided into two parts, the part behind the bisector has a larger opening area than the part preceding the bisector. The opening area of the suction window 23a, including the terminal portion 23d in the rotational direction R, and extending in the rotational direction R by a predetermined distance, has a starting end portion in the rotational direction R ( It is larger than the opening area of the range which extends a predetermined distance in the rotation direction R including 23c).

6, 4 and 5, the suction window 27a which the suction hole 27 opens in the inner peripheral surface 14c of the cylinder part 14 starts an opening with respect to the rotation direction R. As shown to FIG. It extends with the start end part 27c and the end part 27d which complete | opens an opening. The start end portion 27c has a width of a predetermined length in the axial direction. As for the suction window 27a, the axial direction width | variety of the rotating shaft 16 is formed in the terminal part 27d side rather than the start end part 27c side. The axial direction width W4 of the terminal end 27d shown in FIG. 6 is larger than the axial direction width W3 of the start end part 27c. The suction window 27a of this embodiment has the step part 27b in which the axial width of the rotating shaft 16 becomes large rapidly. The axial width of the suction window 27a is relatively smaller on the starting end 27c side than the step portion 27b, and the axial width of the suction window 27a is relatively closer to the terminal end 27d side than the step portion 27b. Big. The suction window 27a is larger than the start end 27c side with respect to the step portion 27b on the end portion 27d side with respect to the step portion 27b.

The suction window 27a is opened larger in the terminal portion 27d than the start end portion 27c. In the case where the length of the rotation direction R of the suction window 27a is bisected, the part behind the bisector has a larger opening area than the part preceding the bisector. The opening area of the suction window 27a including the terminal portion 27d in the rotation direction R and extending a predetermined distance in the rotation direction R is the start end portion in the rotation direction R ( It is larger than the opening area of the range which extends a predetermined distance in the rotation direction R including 27c).

7 is a graph showing the relationship between the rotational phase and the compression chamber volume. The horizontal axis of the graph shown in FIG. 7 shows the rotation phase of the rotating shaft 16 and the rotor 18 which are rotation bodies. The position where the outer circumferential surface of the rotor 18 is in contact with the inner circumferential surface 14c of the cylinder portion 14 is set to a rotational phase of 0 °. The vertical axis of the graph shown in FIG. 7 represents the volume of the compression chamber 21.

When the rotational phase is 0 °, the gap between the outer circumferential surface of the rotor 18 and the inner circumferential surface 14c of the cylinder portion 14 is zero, so the compression chamber volume is zero. As the rotation phase increases from 0 °, the compression chamber volume also gradually increases. In the range below the predetermined rotational phase indicated by both arrows in FIG. 7, the ratio of the compression chamber volume to the increase in the rotational phase is relatively small. When the predetermined rotational phase is exceeded, the ratio of the increase in the compression chamber volume to the increase in the rotational phase increases rapidly.

The suction windows 23a and 27a are formed so that opening area may be comparatively small in the range below the predetermined rotational phase shown by the both arrows in FIG. It is preferable to set the position where the stepped portions 23b and 27b are formed in the rotational direction R to be a rotational phase corresponding to the right end of both arrows shown in FIG. 7. It is preferable that the suction windows 23a and 27a on the trailing side of the rotation direction R are formed in a shape such that the width in the axial direction increases in response to the increase in the compression chamber volume shown in FIG. 7 than the step portions 23b and 27b. desirable.

[Operation of the Compressor 10]

The operation of the compressor 10 will be described below. When the rotating shaft 16 rotates in response to the rotation drive force from a drive source such as a motor or an engine, the rotor 18 rotates in the rotation direction R shown by the arrows in FIGS. 2 and 3. As the rotor 18 rotates, some of the plurality of vanes 19 are pushed out of the vane groove 18a. When the front end surface of the vane 19 is in contact with the inner circumferential surface 14c of the cylinder portion 14, the plurality of compression chambers 21 are partitioned in the cylinder chamber 14d. With the rotation of the rotor 18, the volume in the compression chamber 21 repeats expansion and contraction. Regarding the rotation direction of the rotor 18, the stroke in which the compression chamber 21 enlarges the volume becomes the suction stroke, and the stroke in which the compression chamber 21 reduces the volume becomes the compression stroke.

In the suction stroke, the refrigerant gas is sucked into the suction space 20 from the suction pipe 25 via the suction port 22. At the time of a suction stroke, the compression chamber 21 and the suction space 20 communicate with each other through the suction hole 23, and communicate with each other through the communication path 26 and the suction hole 27. The suction holes 23 and 27 and the communication path 26 comprise the suction path which inhales a refrigerant | coolant in the compression chamber 21 in this embodiment. The refrigerant gas sucked into the suction space 20 passes from the suction window 23a via the suction hole 23 or from the suction window 27a via the communication path 26 and the suction hole 27 in this order. , It is sucked into each compression chamber 21.

In the compression stroke, the refrigerant gas sucked into each compression chamber 21 is compressed by the volume reduction of the compression chamber 21 accompanying the rotation of the rotor 18. The compressed refrigerant gas is discharged from each compression chamber 21 to each discharge chamber 30 via the discharge port 31.

The refrigerant gas in each discharge chamber 30 flows out into the case 36a through the discharge passage 37, is blown out to the outer circumferential surface of the oil separation cylinder 36b, and is rotated around the outer circumferential surface of the oil separation cylinder 36b. It is led downward in 36a. At this time, the lubricating oil is separated from the refrigerant gas by centrifugal separation. The lubricant oil separated from the refrigerant gas moves to the bottom side of the case 36a and is stored in the bottom of the discharge region 35 through the oil passage 36c.

Lubricating oil stored in the bottom of the discharge area 35 is guided to the vane groove 18a from the oil supply passage 15d and pushes the vane 19 to the outer circumferential side as back pressure. The compression chamber 21 is partitioned by the vanes 19 pushed out to the outer circumferential side. On the other hand, in the oil separator 36, the refrigerant gas from which the lubricating oil is separated moves upward of the inside of the oil separation cylinder 36b, and is discharged to the discharge piping 39 through the discharge port 34. As shown in FIG.

[Actions and effects]

Next, the operation and effect of the compressor 10 of the above-described embodiment will be described.

As shown in FIG. 7, in the first half of the suction stroke, the volume of the compression chamber 21 is small, and the increase in the volume of the compression chamber 21 is also small. The increase in the volume of the compression chamber 21 suddenly increases in the middle of the suction stroke, and as a result, the volume of the compression chamber 21 increases in the latter half of the suction stroke.

Therefore, in the compressor 10 of this embodiment, as shown in FIGS. 2-6, the suction windows 23a and 27a which the suction holes 23 and 27 open to the inner peripheral surface 14c of the cylinder part 14 are opened. Silver has a larger axial width in the terminal portions 23d and 27d than the start portions 23c and 27c. The suction windows 23a and 27a monotonically increase in width in the axial direction from the start end portions 23c and 27c toward the end portions 23d and 27d.

In the first half of the suction stroke where the volume of the compression chamber 21 is small, the suction amount to the compression chamber 21 is at least small, and the refrigerant which has not been sucked can be distributed to the suction window on the opposite side with the rotating shaft 16 interposed therebetween. The efficiency can be improved. In the second half of the suction stroke in which the compression chamber 21 has a large volume, since the refrigerant can be sucked into the compression chamber 21 via the suction windows 23a and 27a having a large opening area having an increased axial width, the compression chamber 21 The suction amount of the refrigerant into the 21 can be increased. By varying the suction amount of the refrigerant in response to the volume change of the compression chamber 21, an appropriate amount of refrigerant can be sucked into the compression chamber 21 in response to the suction stroke. As a result, the cooling performance can be improved, and the suction pressure loss of the refrigerant can be reduced, so that power deterioration can be reduced.

The suction window 23a has a stepped portion 23b, and the suction window 27a has a stepped portion 27b, so that the suction window on the side of the end portions 23d, 27d rather than the stepped portions 23b, 27b ( The axial widths of the 23a and 27a can be reliably longer than the axial widths of the suction windows 23a and 27a on the side ends 23c and 27c than the stepped portions 23b and 27b.

(Embodiment 2)

8 is a cross-sectional view of the cylinder portion 14 according to the second embodiment. The suction windows 23a and 27a which open to the inner peripheral surface 14c of the cylinder part 14 of Embodiment 2 are similar to Embodiment 1 in the terminal part 23d, 27d rather than the start part 23c, 27c, Axial width is formed large. The axial width W2 of the terminal end 23d of the suction window 23a is larger than the axial width W1 of the start end 23c. The axial width W4 of the terminal end 27d of the suction window 27a is larger than the axial width W3 of the start end 27c.

The suction windows 23a and 27a of Embodiment 1 have the step part 23b, 27b which the axial width rapidly expands in the middle of the rotation direction R. As shown in FIG. On the other hand, the suction windows 23a and 27a of Embodiment 2 do not have a step part.

In the suction windows 23a and 27a of the second embodiment, the axial width of the rotor 18 is increasing from the start end portions 23c and 27c toward the end portions 23d and 27d. The suction window 23a is formed from the back end part 23c side to the end part 23d side to the position which falls further back from the rear surface 13s of the bottom wall part 13a. The suction window 27a is formed in the position which falls further from the open end 14e of the cylinder part 14 toward the end part 27d side from the start end part 27c side. As a result, the suction windows 23a and 27a of the second embodiment gradually expand in the axial width from the start end portions 23c and 27c toward the end portions 23d and 27d.

Similarly to the first embodiment, the compressor 10 according to the second embodiment in which the above-described suction windows 23a and 27a are formed also has a large suction area in the latter half of the suction stroke having a large volume of the compression chamber 21. Since the refrigerant can be sucked into the compression chamber 21 via the windows 23a and 27a, the suction amount of the refrigerant into the compression chamber 21 can be increased. By gradually expanding the axial widths of the suction windows 23a and 27a without rapidly expanding, the suction amount of the refrigerant into the compression chamber 21 can be adjusted more appropriately in response to the volume change of the compression chamber 21.

(Embodiment 3)

9 is a cross-sectional view of the cylinder portion 14 according to the third embodiment. The suction windows 23a and 27a which open to the inner peripheral surface 14c of the cylinder part 14 of Embodiment 3 are similar to Embodiment 1 in the terminal part 23d, 27d rather than the start part 23c, 27c, Axial width is formed large. The axial width W2 of the terminal end 23d of the suction window 23a is larger than the axial width W1 of the start end 23c. The axial width W4 of the terminal end 27d of the suction window 27a is larger than the axial width W3 of the start end 27c.

In Embodiments 1 and 2, the pair of suction windows 23a and 27a have a symmetrical shape in the axial direction (left and right directions in FIGS. 6 and 8) of the rotor 18. In contrast, in the third embodiment, the suction window 23a and the suction window 27a have an asymmetrical shape in the axial direction. In detail, the suction window 23a formed in the front in the axial direction has the same shape as the suction window 23a of the first embodiment. The suction window 27a formed rearward in the axial direction is larger than the suction window 27a of the first embodiment on the side of the end portion 27d than the step portion 27b. Therefore, the suction window 27a of Embodiment 3 has an opening area larger than the suction window 23a.

As described with reference to FIG. 1, the suction space 20 and the suction port 22 through which the refrigerant flowing into the suction holes 23 and 27 pass are formed on the front side in the axial direction of the rotation shaft 16. It is. In Embodiment 3, the suction window 27a of the back side in the axial direction of the side in which the suction space 20 and the suction port 22 are not formed in the axial direction is the front side in the axial direction. The width in the axial direction is larger than that of the suction window 23a. The axial width W4 of the terminal part 27d of the suction window 27a shown in FIG. 9 is larger than the axial width W2 of the terminal part 23d of the suction window 23a.

The suction hole 23 communicates directly with the suction space 20, while the suction hole 27 communicates with the suction space 20 via the communication path 26. The path until reaching the suction window 27a is longer than the path until reaching the suction window 23a. If the suction window 23a and the suction window 27a have a symmetrical shape, the suction window 23a and the suction window 27a are sucked from the suction window 27a into the compression chamber 21 because of the pressure loss difference in the path until reaching the suction windows 23a and 27a. The flow rate of the refrigerant to be used becomes relatively small. Therefore, in Embodiment 3, the suction window 27a which is further from the suction space 20 and the suction port 22 has a larger opening area than the suction window 23a.

By configuring in this way, the difference of the pressure loss of the refrigerant | coolant in the path | route until it reaches the suction window 27a, and the pressure loss of the refrigerant | coolant in the path | route until it reaches the suction window 23a becomes small, The uniformity of the flow volume of the refrigerant flowing into the compression chamber 21 from both the suction windows 23a and 27a is improved. As a result, the refrigerant can be sucked into the compression chamber 21 more efficiently, and the pulsation of the density of the refrigerant sucked into the compression chamber 21 can be suppressed.

(Embodiment 4)

10 is a cross-sectional view of the cylinder portion 14 according to the fourth embodiment. The suction window 23a opening in the inner circumferential surface 14c of the cylinder portion 14 of the fourth embodiment has a larger axial width in the terminal portion 23d than the start portion 23c in the same manner as in the first embodiment. It is. The axial width W2 of the terminal end 23d of the suction window 23a is larger than the axial width W1 of the start end 23c.

In the structure of Embodiment 1, the suction window 23a and the suction window 27a are formed in the axial direction of the rotor 18. As shown in FIG. In contrast, in Embodiment 4, the suction window 27a is not formed. One suction window 23a in the axial direction of the rotor 18 at a position spaced apart from the rear face 13s of the bottom wall portion 13a and spaced apart from the open end 14e of the cylinder portion 14. Is formed. The suction window 23a is formed behind the rear face 13s of the bottom wall part 13a, and in the position ahead of the open end 14e of the cylinder part 14. The suction window 23a has a stepped portion 23b in which the axial width rapidly expands.

Similarly to the first embodiment, the compressor 10 according to the fourth embodiment in which the above-described suction window 23a is formed also has a suction window having a large opening area in the latter half of the suction stroke having a large volume of the compression chamber 21. Since the refrigerant can be sucked into the compression chamber 21 via 23a), the suction amount of the refrigerant into the compression chamber 21 can be increased. Since it is the structure which forms one suction hole 23 in the position away from the bottom wall part 13a, the process of the suction hole 23 becomes easier.

(Embodiment 5)

11 is a cross-sectional view of the cylinder portion 14 according to the fifth embodiment. The suction window 23a opening in the inner circumferential surface 14c of the cylinder portion 14 of the fifth embodiment is larger in the axial width in the terminal portion 23d than the start end portion 23c in the same manner as in the fourth embodiment. It is. The axial width W2 of the terminal end 23d of the suction window 23a is larger than the axial width W1 of the start end 23c.

In Embodiment 4, the suction window 23a has the symmetrical shape in the axial direction (left-right direction in FIG. 10) of the rotor 18. As shown in FIG. In contrast, in Embodiment 5, the suction window 23a has an asymmetrical shape. In detail, the length in which the suction window 23a extends rearward is larger than the length in which the suction window 23a extends forward from the end 23d side than the step 23b. The suction window 23a is inflated toward the rear side at the terminal 23d side. Therefore, the suction window 23a of Embodiment 5 has the opening area larger than the front side of an axial direction in the back side of the rotor 18 in the axial direction.

By configuring in this way, the uniformity of the flow volume of the refrigerant | coolant which flows into the compression chamber 21 improves in the front side and the back side of the rotor 18 like the third embodiment. As a result, the refrigerant can be sucked into the compression chamber 21 more efficiently, and the pulsation of the density of the refrigerant sucked into the compression chamber 21 can be suppressed.

In the foregoing description, the example in which the bottom wall portion 13a and the cylinder portion 14 are formed integrally has been described. Instead of this example, the rear side plate 15 and the cylinder part 14 may be integrally formed, and the bottom wall part 13a may be fixed to the front end part of the cylinder part 14, or You may comprise the cylinder part 14, the rear side plate 15, and the front side plate as both a separate member.

As mentioned above, although embodiment was described, the said indication is an illustration and restrictive at no points. The technical scope of the present invention is shown by the claims, and it is intended that the meanings and equivalents of the claims and all the changes within the scope are included.

10: compressor
11: housing
12: rear housing
13: front housing
13a: bottom wall
13s: rear side
14: cylinder part
14a, 14b: recess
14c: inner circumference
14d: cylinder chamber
14e: open end
15: rear side plate
15s: front side
16: axis of rotation
18: rotor
18a: vane groove
19: vane
20: suction space
21: compression chamber
22: suction port
23, 27: suction hole
23a, 27a: suction window
23b, 27b: stepped portion
23c, 27c: start end
23d, 27d: termination
26: communication path
30: discharge chamber
31: discharge port
32: discharge valve
34: discharge port
35: discharge area
36: oil separator
37: discharge passage
141b: extension forming surface
142b: mounting surface
R: direction of rotation
W1, W2, W3, W4: Axial Width

Claims (7)

A cylindrical cylinder portion having an inner circumferential surface,
A partition wall partitioning a cylinder chamber inside the cylinder portion;
A rotating shaft rotatably formed in the cylinder chamber,
A rotor connected to the rotating shaft and having a plurality of vane grooves formed on an outer circumference thereof;
Vanes mounted on each of the plurality of vane grooves so as to be sunk,
A compression chamber partitioned by said partition wall, said rotor, and said vane in said cylinder chamber,
A suction passage through which the refrigerant is sucked into the compression chamber;
The suction passage is provided with a suction window opened in the inner circumferential surface,
The suction window extends with an axial width in the axial direction of the rotor, with a starting end and an end terminating the opening with respect to the rotational direction of the rotor.
A vane type compressor, wherein the longest part of the axial width of the suction window is near the end portion (the end side side). The method of claim 1,
A vane type compressor, wherein the end portion has an axial width longer than a predetermined width of the start end portion. The method according to claim 1 or 2,
The said suction window has the said axial width long by the step part at the said terminal part side, The vane type compressor. The method according to claim 1 or 2,
A suction port communicating with the suction passage and sucking refrigerant from the outside;
The said suction window is a vane type compressor which expands toward the direction which falls away from the said suction port by the said end part side. The method according to claim 1 or 2,
A suction port communicating with the suction passage and sucking refrigerant from the outside;
The said suction window is formed in pair in the axial direction of the said rotor,
A vane type compressor having a larger opening area of a suction window farther from the suction port among the pair of suction windows. The method according to claim 1 or 2,
The vane type compressor, wherein the suction window gradually increases in the axial direction of the rotor toward the end side in the rotational direction. The method according to claim 1 or 2,
The vane type compressor of the said suction window in the circumferential direction of the said rotating shaft is smaller than the distance between the adjacent vane grooves in the circumferential direction of the said rotating shaft.

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