KR100552312B1 - Inlet and outlet of refrigerant compressor - Google Patents

Abstract

The present invention relates to an improvement in the shape of the discharge port and the suction port in order to suppress the formation of turbulent flow in the flow of the refrigerant gas. The shape of the discharge port according to the present invention has a side wall made of a surface inclined such that the size of the discharge port outer circumference gradually increases from the surface of the piston cylinder to the surface of the discharge chamber. Similarly, the shape of the suction port according to the present invention has a side wall made of a sloped surface such that the size of the suction port outer circumference gradually increases from the surface of the suction chamber to the surface of the piston cylinder. By providing sidewalls of inclined surfaces in accordance with the present invention, the flow path of the refrigerant gas is formed in a direction almost tangent to the reed valve. By reducing the flow resistance of the discharge port or the suction port, the volumetric efficiency of the compressor is improved and the noise of the compressor is reduced.

Description

Inlet and outlet of refrigerant compressor

TECHNICAL FIELD The present invention relates to a refrigerant compressor for use in an air condition system of an automobile. More specifically, the present invention relates to the shape of a suction hole and a discharge hole provided in the valve plate of the compressor.

The structure and operation of the refrigerant compressor used in the automotive air condition system are as follows. 1, a conventional compressor 100 is shown. The compressor 100 has a front housing 30, a housing 27, a valve plate 1, and a rear housing 32. A drive shaft 34 is installed along the central axis of the compressor 100, and the drive shaft is rotatably supported by the needle bearings 35 and 36. The cam rotor 37 fixed to the drive shaft 34 meshes with the inner wall of the front housing 30 via the thrust bearing 38 in the housing 27. When the drive shaft 34 rotates, the cam rotor 37 also rotates. The hinge mechanism 39 couples the cam rotor 37 to the inclined plate 40. This inclined plate 40 rotates with the cam rotor 37. The wobble plate 43 is engaged with the inclined plate 40 via the thrust bearing 41 and the needle bearing 42. Since the rocking motion occurs in the inclined plate 40, the inclined plate 40 is rocked while rotating. The movement of the inclined plate 40 is transmitted to the swinging plate 43. Rotation of the swinging plate 43 is suppressed by engagement with the guide bar 44. Therefore, only the rocking motion during the movement of the inclined plate 40 is transmitted from the inclined plate 40 to the rocking plate 43. The swing plate 43 oscillates but does not rotate with the drive shaft 34. The rod 45 is connected to the swing plate 43 and the plurality of pistons 46 by spherical coupling. When the swinging plate 43 swings, each piston 46 reciprocates in one of the plurality of cylinders 71.

The suction reed valve 22, the discharge reed valve 2 and the retainer 3 are fixed to the valve plate 1 by bolts 47. The suction port 5 and the discharge port 4 are provided in each piston cylinder. The suction chamber 72 and the discharge chamber 70 are formed by the valve plate 1 and the rear housing 32, and are separated by the inner partition plate 33.

When the drive shaft 34 is rotated by an external power source (not shown), each piston 46 is reciprocated in the corresponding piston cylinder 71. An intake stroke is executed when the piston 46 moves in the left direction in FIG. 1, and a compression stroke is executed when the piston 46 moves in the right direction.

In the intake stroke, the refrigerant gas in the suction chamber 72 is sucked into the piston cylinder 71 through the suction port 5. Due to the pressure change between the suction chamber 72 and the discharge chamber 71, the refrigerant gas in the suction chamber 72 flows to the suction port 5, and passes through the suction port 5 to open the suction reed valve 22. Inflow to the piston cylinder (71). The suction reed valve 22 suppresses the backflow of the refrigerant gas directed to the suction chamber 72 during the compression stroke.

In the compression stroke, the refrigerant gas of the cylinder 71 is discharged to the discharge chamber 70 through the discharge port 4. Due to the pressure change between the piston cylinder 71 and the discharge chamber 70, the refrigerant gas flows through the discharge port 4, opens the discharge lead valve 2, and flows into the discharge chamber 70. The discharge reed valve 2 prevents backflow of the refrigerant gas directed to the suction chamber 72 during the intake stroke.

FIG. 2A shows a cross section of the valve plate 1 viewed from the rear housing side. 2B shows a cross section of the valve plate 1 viewed from the cylinder head side. As shown in FIG. 2A, the rear housing 32 is fixed to the housing 27 by a plurality of bolts 13. The suction port 5 and the discharge port 4 are arranged at an angle around the center CO, which is a position coinciding with the piston cylinder 71. The suction chamber 72 and the discharge chamber 70 are partitioned by the inner partition plate 33. The discharge reed valve 2 provided in the inner partition plate 33 has a substantially star shape. The arm of the discharge reed valve 2 covers the discharge port 4. As shown in FIG. 2B, the suction reed valve 22 also has a star shape. In each arm, a hole 22h is provided to allow the discharge gas to flow therethrough.

3 shows the valve plate viewed from the valve plate 1 side facing the discharge chamber 7. The discharge port 4 and the suction port 5 are disposed at an angle with respect to the center C of the valve plate 1. 4 and 5 show radial cross sections of the valve plate 1 shown in FIG. 1, respectively. The reed valve 2 is fixed between the valve plate 1 and the valve retainer 3. The discharge port 4 has side walls substantially perpendicular to both side surfaces of the valve plate 1.

4 and 5 show the valve plate 1 during the compression stroke. When the refrigerant gas is discharged from the cylinder 71, the refrigerant gas collides with the reed valve 2 to move the valve. The refrigerant gas flows into the discharge chamber 70 through a gap formed between the reed valve 2 and the valve plate 1. When the flow of the refrigerant gas collides with the reed valve 2 shown in FIG. 4, the flow path of the refrigerant gas is switched substantially perpendicular to the valve plate 1. By such a rapid change in the flow direction, turbulence may occur in the refrigerant gas flow. Moreover, part of the refrigerant gas flow that collides with the reed valve 2 may not flow into the discharge chamber 70 but may instead return to the piston cylinder 71. The effect of this turbulence is indicated by arrows in FIGS. 4 and 5. Therefore, turbulent motion of the refrigerant gas results in flow resistance at the discharge port 4. This flow resistance degrades volumetric efficiency and major evaluated performance of the compressor 100. In addition, the turbulent motion interferes with the operation of the reed valve 2, which hinders the reed valve 2 from being accurate and complete opening and closing. Moreover, turbulent flow at the discharge port 4 causes noise generated in the compressor 100. Similar problems occur in the inlet 5 as well.

Therefore, many efforts have been made to efficiently solve the turbulence formation problem of the refrigerant gas flow passing through the inlet and outlet and to suppress the noise caused by this.

In order to efficiently solve the turbulent flow formation problem in the refrigerant gas flowing through the inlet and outlet, it is required to suppress the noise of the compressor without disturbing the flow of the refrigerant gas. Accordingly, it is an object of the present invention to provide inlet and outlet ports on the valve plate of the compressor which have a shape that can improve the volumetric efficiency of the compressor and reduce the noise of the compressor. Another object of the present invention is to provide a suction port and a discharge port having a shape capable of suppressing the turbulence of the refrigerant gas to lower the flow resistance of the refrigerant gas passing through the suction port or the discharge port or both.

The compressor according to the present invention includes a valve plate provided with a suction passage and a discharge passage. In the discharge passage, each discharge passage has a first piston cylinder side opening having a predetermined area, a discharge chamber side opening having a predetermined area, and sidewalls extending between the openings. At least a portion of the discharge passage side walls are inclined. The area of the discharge chamber side opening is larger than the area of the first piston cylinder side opening. In the suction passage, each suction passage has a second piston cylinder side opening having a predetermined area, a suction chamber side opening having a predetermined area, and a side wall extending between the openings. At least a portion of the suction passage sidewalls are inclined. The area of the piston cylinder side opening is larger than the area of the suction chamber side opening. The side walls of the passages comprise a substantially cylindrical portion. Moreover, the thickness of the inclined portion of the passage sidewall may be smaller than the thickness of the valve plate. Although partially inclined, the object of the present invention can be achieved.

The flow path of the refrigerant gas may be gradually curved along the inclined sidewalls of the inlet or outlet or both. The flow path of the refrigerant gas does not impinge vertically with the reed valve but instead travels along the inclined portion of the side wall. As a result, the turbulence of the flow of the refrigerant gas is reduced at the inlet or outlet to improve the volumetric efficiency of the compressor and to suppress the noise of the compressor associated with it.

The objects and advantages of the present invention will become apparent to those skilled in the art upon consideration of the following detailed description with reference to the accompanying drawings.

In the exemplary embodiments of the present invention shown in FIGS. 6 to 25, the same reference numerals are used for the same elements. Details of the various embodiments of the present invention corresponding to the conventional compressor and features thereof are as described above, and thus will be omitted below.

FIG. 6 is a plan view of the valve plate 11 viewed from the discharge chamber 70 side according to an embodiment of the present invention. In the valve plate 11, the discharge port 14 and the suction port 15 are disposed so as to conform to the center C. As shown in FIG. 7 and 8 show the cross section of the discharge mechanism during the compression stroke. The reed valve 12 is fixed between the valve plate 11 and the valve retainer 13. The side wall 16 of the discharge port 14 is formed in the convex inclined surface. On the piston cylinder side end part of this side wall 16, the circular introduction port 16a is provided. Further, a circular large opening 16b is provided on the discharge chamber side end of the side wall 16. As shown in Fig. 9, the area of the circular introduction port 16a is denoted by Sa, and the area of the circular large opening 16b is denoted by Sb, respectively.

According to one embodiment of the invention, area Sb is about 1.5 times larger than area Sa. The area Sa of the piston cylinder side surface of the valve plate 11 gradually increases to the area Sb of the discharge chamber side surface of the valve plate 11 by the curved surface of the side wall 16. Therefore, the size of the outer periphery of the discharge port 14 becomes larger gradually from the piston cylinder side surface of the valve plate 11 to the discharge chamber side surface of the valve plate 11. According to the present invention, a viscous fluid flowing near the wall of the chamber or tube flows along the surfaces. Since the refrigerant gas is a viscous fluid, when the discharge port 14 is opened, the refrigerant gas flows along the side wall 16 as shown by the arrows in FIGS. 7 and 8. The flow direction of the refrigerant gas is gradually curved in the lateral direction of FIGS. 7 and 8. Therefore, the refrigerant gas is prevented from directly colliding with the reed valve 12. As a result, turbulence generation of the refrigerant gas at the discharge port is reduced. Therefore, the volume efficiency of the compressor 100 is increased due to the shape of the discharge port 14.

10 to 13 show yet another embodiment of the present invention. In particular, in Fig. 10, a plan view of the valve plate 11 seen from the discharge chamber side is shown. In the valve plate 11, the discharge port 14 'and the suction port 15 are disposed so as to conform to the center C. As shown in FIG. 11 and 12 are sectional views showing the discharge mechanism during the compression stroke. The reed valve 12 is fixed between the valve plate 11 and the valve retainer 13. The discharge port 14 'includes a partially convex side wall 16' and a cylindrical portion 19 '. A circular introduction port 16a 'is provided at the piston cylinder side outer peripheral portion of the side wall 16'. In addition, an elliptical large opening 16b 'is provided in the opening of the discharge chamber side end of the side wall 16'.

According to this embodiment, the elliptical opening 16b 'only extends to the radially outer surface of the discharge port 14' with respect to the center C of the valve plate 11. As shown in Fig. 13, the area of the circular introduction port 16a 'is indicated by Sa', and the area of the elliptical opening 16b 'is indicated by Sb', respectively. According to this embodiment, the area Sb 'is about 1.5 times larger than the area Sa'. The area Sa 'of the piston cylinder side surface of the valve plate 11 gradually increases to the area Sb' of the discharge chamber side surface of the valve plate 11 due to the curved surface of the inclined side wall 16 '. Therefore, the size of the outer periphery of the discharge port 14 'becomes larger from the piston cylinder side surface of the valve plate 11 to the discharge chamber side surface of the valve plate 11.

14 to 17 show another embodiment of the present invention. In particular, FIG. 14 shows a plan view of the valve plate 11 viewed from the discharge chamber side. In the valve plate 11, the discharge port 14 '' and the suction port 15 are disposed so as to conform to the center C. As shown in FIG. On the surface of the valve plate 11, a valve seating groove 110 is provided around each discharge port 14 ″. This valve seating groove 110 prevents the reed valve 12 from sticking to the valve plate 11.

15 and 16 are cross-sectional views showing the discharge mechanism during the compression stroke. The reed valve 12 is fixed between the valve plate 11 and the valve retainer 13. The discharge port 14 '' includes an inclined sidewall 16 '' and a vertical portion 17 ''. The opening of the piston cylinder side end part of the said vertical part 17 "is provided with the circular introduction port 16a". Moreover, the circular opening 16b is provided in the opening of the discharge chamber side edge part of the said side wall 16 ".

As shown in FIG. 17, the area of the circular introduction port 16a ″ is denoted by Sa ″ and the area of the circular large opening 16b ″ is denoted by Sb ″, respectively. For this embodiment, the area Sb '' is about 1.5 times larger than the area Sa ''. Therefore, the area Sa '' of the piston cylinder side surface of the valve plate 11 gradually expands to the area Sb '' of the discharge chamber side surface of the valve plate 11 by the inclined side wall 16 ''. Moreover, the height of the vertical portion 17 '' shown in FIG. 16 becomes zero or more.

18 to 21 show yet another embodiment of the present invention. In particular, in FIG. 18, the top view of the valve plate 11 seen from the discharge chamber side is shown. In the valve plate 11, the discharge port 14 '' 'and the suction port 15 are disposed at a right angle with respect to the center C. As shown in FIG. 19 and 20 are cross-sectional views showing the discharge mechanism during the compression stroke. The reed valve 12 is fixed between the valve plate 11 and the valve retainer 13. The outlet 14 '' 'consists of an inclined sidewall 16' '', a cylindrical portion 19 '' 'and a vertical portion 17' ''. A circular introduction port 16a '' 'is provided at the opening of the piston cylinder side end portion of the vertical portion 17' ''. Further, an elliptical opening 16b '' 'is provided in the opening at the discharge chamber side end of the inclined side wall 16' ''.

In the case of this embodiment, the elliptical opening 16b '' 'extends radially outwardly of the outlet 14' '' with respect to the center C of the valve plate 11. As shown in Fig. 21, the area of the circular inlet 16a '' 'is indicated by Sa' '' and the area of the elliptical opening 16b '' 'by Sb' '', respectively. . For this embodiment, the area Sb '' 'is about 1.5 times larger than the area Sa' ''. Therefore, the area Sa '' 'of the piston cylinder side surface of the valve plate 11 gradually becomes the area Sb' '' of the discharge chamber side surface of the valve plate 11 by the partially inclined side wall 16 '' '. Increases.

22 to 25 show yet another embodiment of the present invention. In particular, in FIG. 22, the top view of the valve plate 21 seen from the piston cylinder side is shown. In the valve plate 21, the discharge port 24 and the suction port 25 are disposed so as to conform to the center C. As shown in FIG. 23 and 24 are sectional views showing the suction mechanism during the suction stroke. As shown in FIG. 23, the vibration of the reed valve 22 is suppressed by the groove 23 formed at the end of the housing 27. Inlet 25 has convexly inclined sidewalls 26. A circular introduction port 26a is provided in the opening at the suction chamber side end of the inclined side wall 26. Moreover, the circular large opening 26b is provided in the opening of the piston cylinder side edge part of the said inclined side wall 26. As shown in FIG.

As shown in Fig. 25, the area of the circular introduction port 26a is denoted by S2a, and the area of the circular large opening 26b is denoted by S2b, respectively. For this embodiment, area S2b is about 1.5 times larger than area S2a. The curved surface of the side wall 26 which is inclined convexly increases the area S2b of the suction chamber side surface of the valve plate 21 to the area S2b of the piston cylinder side surface of the valve plate 21. Therefore, the size of the outer circumference of the suction port 25 becomes larger from the suction chamber side surface of the valve plate 21 to the piston cylinder surface. Although the openings shown in Figs. 6-21 relate to the shape and structure of the discharge port, this shape and structure can be applied to the suction port as well.

The present invention is applicable to all kinds of compressors having a reed valve mechanism. For example, the present invention can be applied to a rotary inclined plate compressor, a rocking plate compressor or a scroll compressor. The present invention has been described above through the preferred embodiments, but is not limited to these embodiments. Those skilled in the art should understand that various changes and modifications are possible within the scope of the appended claims and the spirit of the invention.

The present invention provides convex and inclined sidewalls or inclined sidewalls having cylindrical portions at the discharge or intake ports or both. As a result, it is possible to reduce the occurrence of turbulence in the refrigerant flow through the discharge port, the suction port, or both. Therefore, since the flow resistance of the refrigerant gas passing through the discharge port and the suction port is reduced, it is possible to improve the volumetric efficiency of the compressor and to reduce the noise of the compressor in this regard.

1 is a cross-sectional view showing a conventional compressor.

2A is a cross-sectional view taken along the line IIa-IIa of FIG. 1.

FIG. 2B is a cross-sectional view taken along the line IIb-IIb of FIG. 1. FIG.

3 is a plan view of the valve plate shown in FIG.

4 is a cross-sectional view taken along the line IV-IV of the valve plate shown in FIG.

FIG. 5 is a cross-sectional view taken along the line VV of the valve plate shown in FIG. 3. FIG.

Figure 6 is a plan view showing a valve plate according to an embodiment of the present invention.

FIG. 7 is a cross-sectional view taken along the line VIII-VIII of the valve plate shown in FIG. 6. FIG.

FIG. 8 is a cross-sectional view taken along the line VIII-VIII of the valve plate shown in FIG. 6. FIG.

9 is a partial plan view of the discharge port shown in FIG. 6;

10 is a plan view showing a valve plate according to another embodiment of the present invention.

FIG. 11 is a cross-sectional view taken along the line VI-XI of the valve plate shown in FIG. 10; FIG.

12 is a cross-sectional view taken along the line XII-XII of the valve plate shown in FIG. 10.

FIG. 13 is a partial plan view of the discharge port shown in FIG. 10; FIG.

14 is a plan view showing a valve plate according to another embodiment of the present invention.

FIG. 15 is a cross-sectional view taken along the line XV-XV of the valve plate shown in FIG. 14. FIG.

FIG. 16 is a cross-sectional view taken along the line VIVI-VI of the valve plate shown in FIG. 14; FIG.

FIG. 17 is a partial plan view of the discharge port shown in FIG. 14; FIG.

18 is a plan view showing a valve plate according to another embodiment of the present invention.

FIG. 19 is a cross-sectional view taken along the line VII-VII of the valve plate shown in FIG. 18; FIG.

20 is a cross-sectional view taken along the line VIII-VIII of the valve plate shown in FIG. 18.

FIG. 21 is a partial plan view of the discharge port shown in FIG. 18; FIG.

Figure 22 is a plan view showing a valve plate according to another embodiment of the present invention.

FIG. 23 is a cross-sectional view taken along the line XIII-XIII of the valve plate shown in FIG. 22; FIG.

FIG. 24 is a cross-sectional view taken along the line XIV-XIV of the valve plate shown in FIG. 22. FIG.

FIG. 25 is a partial plan view of the discharge port shown in FIG. 22; FIG.

<Explanation of symbols for main parts of drawing>

11: valve plate

12: reed valve

13: valve retainer

14 discharge port

15: inlet

16: sidewalls

16a: circular introduction

16b: circular large opening

70 discharge chamber

100: compressor

Claims (12)

A compressor having a discharge valve mechanism, A valve plate having at least one discharge passage for providing fluid communication between the piston cylinder and the discharge chamber, a discharge reed valve, and a valve retainer, The at least one discharge passage having a first piston cylinder side opening having a predetermined area, a discharge chamber side opening having a predetermined area, and a sidewall extending between the openings, at least a portion of the discharge passage sidewall Inclined, the area of the discharge chamber side opening is larger than the area of the first piston cylinder side opening, A suction valve mechanism is further included, wherein the suction valve mechanism suppresses movement of at least one suction passage, a suction reed valve, and the suction reed valve for providing fluid communication between the suction chamber and the piston cylinder. And a valve plate with means, wherein the at least one suction passage has a second piston cylinder side opening having a predetermined area. A suction chamber side opening having a predetermined area, and a side wall extending between the openings, at least a part of the side wall of the suction passage is inclined, and an area of the second piston cylinder side opening is an area of the suction chamber side opening; Compressor, characterized in that larger than. The compressor according to claim 1, wherein the valve plate has a predetermined thickness such that the valve plate has a thickness greater than the height of the inclined side wall, and the inclined discharge passage side wall portion has a predetermined height. The compressor of claim 1, wherein the sidewalls of the discharge passage further comprise a substantially cylindrical portion. The compressor as set forth in claim 1, wherein said first piston cylinder side opening has a circular outer circumferential shape. The compressor according to claim 1, wherein the discharge chamber side opening has a circular outer circumferential shape. The compressor according to claim 1, wherein the discharge chamber side opening has an elliptical outer circumferential shape. A compressor having a suction valve mechanism, A valve plate having at least one suction passage for providing fluid communication between the suction chamber and the piston cylinder, a suction reed valve, and means for inhibiting movement of the suction reed valve, the at least one The suction passage has a first piston cylinder side opening having a predetermined area, a suction chamber side opening having a predetermined area, and a side wall extending between the openings, at least a part of the suction passage side wall being inclined, The area of the opening of the first piston cylinder side is larger than the area of the opening of the suction chamber side, Further comprising a discharge valve mechanism, wherein the discharge valve mechanism includes the valve plate having at least one discharge path, a discharge reed valve, and a valve retainer for providing fluid communication between the discharge chamber and the piston cylinder, The at least one discharge path having a second piston cylinder side opening having a predetermined area, an discharge chamber side opening having a predetermined area, and sidewalls extending between the openings, the at least part of the sidewall of the discharge passage Is inclined, and the area of the discharge chamber side opening is larger than the area of the second piston cylinder side opening, The compressor according to claim 7, wherein the valve plate has a predetermined thickness such that the thickness of the valve plate is greater than the height of the inclined sidewall, and the inclined suction passage sidewall portion has a predetermined height. 8. The compressor of claim 7, wherein the side wall of the suction passage further comprises a substantially cylindrical portion. The compressor according to claim 7, wherein the suction chamber side opening has a circular outer circumferential shape. 8. The compressor as claimed in claim 7, wherein the piston cylinder side opening has a circular outer circumferential shape. 8. The compressor as claimed in claim 7, wherein the piston cylinder side opening has an elliptical outer circumferential shape.