Valved discharge mechanism of a fluid displacement apparatus

Abstract: A fluid displacement apparatus comprises a valve plate member dividing into a first chamber and a second chamber comprising a discharge chamber. A passage is formed in the valve plate member and communicates the first chamber with the discharge chamber. An elastic valve member is disposed on the valve plate and is capable of bending to open and close the end opening of the passage. The valve retainer member is secured to the valve plate together with the elastic valve member by a securing means and has a curved portion formed at a extreme portion of the valve retainer member. The valve seat includes a recessed portion offset from end surface of the valve plate. The recessed portion includes a inclined portion and a wall portion extending therefrom. A first distance formed between a beginning portion of the curved portion of the valve retainer member and the securing means is greater than a second distance formed between an edge portion of the recessed portion of the valve seat and the securing means. Noise and vibration caused by the striking of discharge reed valve against the valve seat and the retainer member are thus decreased.

Description: The present invention relates to a fluid displacement apparatus, more particularly, to a valved discharge mechanism of a refrigerant compressor used in an automotive air conditioning system. The valved discharged mechanism of a refrigerant compressor are well known in the prior art. For example, Figure 1 depicts a valved discharge mechanism used in a refrigerant compressor as described in U.S. Fat. No.4,978,285. As disclosed therein, a refrigerant compressor includes a compressor housing defining a compression chamber in which successive strokes of intake, compressing, and discharge of a refrigerant gas are repeatedly performed. Further, the compressor includes valve plate 65, which partitions the compression chamber and the discharge chamber, and a discharge valve assembly, which is mounted on an end surface of valve plate 65. Valve plate 65 has discharge hole 652 extending therethrough to allow communication of the compression chamber with the discharge chamber. The discharge valve assembly includes discharge reed valve 81 and valve retainer 80, which are secured together to end surface 65a of valve plate 65 by fixing bolt 82. Discharge reed valve 81, which is made of an elastic material, regulates the flow of the refrigerant gas and makes sealing contact engages end surface 65a of valve plate 65 when the operation of compressor is stopped. Valve retainer 80 limits the bending movement of discharge reed valve 81 in the direction in which the refrigerant gas exits the compression chamber and enters the discharge chamber through discharge hole 652. Discharge reed valve 8i has a predetermined value of elastic modulus which keeps discharge hole 652 closed until the pressure in the compression chamber reaches a predetermined value. In such arrangement, discharge reed valve 81 strikes retainer 80 when it opens, and strikes end surface 65a of valve plate 65 when it closes. A compressor with such a discharge valve arrangement generates vibration and noise during operation of the compressor due to this striking. Vibration and noise caused by reed valve 81 striking end surface 65a of valve plate 65 are particularly disadvantageous, i.e., readily transmitted to the compress housing. One solution attempted by the assignee of the present application in EP-A-697521 is depicted Figure 2. This is prior art under Article 54(3) only. There, valve plate 65 includes recessed portion 650 formed so that its depth increases with distance from point B, which is located on valve plate 65 and is spaced a distance L from fixing bolt 82. Recessed portion 650 includes curved surface 651 surrounding discharge hole 652. When discharge reed valve 81 is in its closed position, it sealingly engages inclined surface 651. Curved surface 651 has a radius of curvature R1, which defines the closing deformation of discharge reed valve 81. Further, retainer 80 includes curved surface 80a having radius of curvature R2, which defines the opening deformation of discharge reed valve 81. Radius of curvature R1 is designed to be equal to or less than radius of curvature R2 so that when reed valve 81 closes, its elastic restoring force will not cause it to strike end surface 65a of valve plate 65. Curved surface 80a of retainer 80 begins curving away from valve plate 65 at point A, which is also spaced at distance L from bolt 82. In this arrangement, the impact force with which discharge reed valve 81 strikes curved surface 651 of valve plate 65 is smaller than that which discharge reed valve 81 strikes retainer 80. This occurs because in the arrangement of Figure 2, discharge reed valve 81 returns to its closed position primarily due to the pressure difference between the cylinder chamber and the discharge chamber rather than because of the elastic restoring force of discharge reed valve 81. Therefore, noise and vibration which are caused by the striking of discharge reed valve 81 are reduced in comparison with the arrangement of Figure 1. However, this arrangement dose not a account for noise and vibration which discharge reed valve 81 causes when discharge reed valve 81 strikes retainer 80. As a result, vibration and noise propagate to the passenger compartment. It is all object of the present invention to provide a fluid displacement apparatus for use in an automotive air conditioning system having a valved discharge mechanism which can effectively reduce the vibration noise emitting from a discharge vale assembly and thus, reduce the propagation of an offensive noise to a passenger compartment of a vehicle. It is a further object of the present invention to provide a fluid displacement apparatus wherein volumetric efficiency is improved. FR-A-699434 discloses a fluid displacement apparatus comprising: a housing including a front end plate and a rear end plate; a valve plate member disposed in the housing and dividing the housing into a first chamber and a second chamber, the second chamber comprising a discharge chamber; a passage formed in the valve plate member extending between the first chamber and the discharge chamber, the passage having an open end through which discharge fluid flows; an elastic valve member disposed on the valve plate, the valve member having a spring constant causing the passage to remain blocked until the pressure in the first chamber reaches a predetermined value; a valve retainer member secured by a securing member to the valve plate, the valve retainer member bent away from the valve plate, the valve retainer member limiting bending movement of the valve member, and a valve seat formed on the valve plate around the open end of the passage, the valve seat comprising a recess formed in the valve plate, the recess including a surface inclined with increasing depth in radial direction of the valve plate. According to the present invention, such an apparatus is characterised by the inclined surface beginning at a point radially outside the securing member and the point at which the valve retainer member is bent being radially outside the point where the inclined surface begins. Further objects, features and other aspects of the present invention will be understood from the detailed description of the preferred embodiment of the present invention with reference to the annexed drawings. In the accompanying drawings:- Figure 1 is an enlarged sectional view of a discharge valve assembly in accordance with one prior art. Figure 2 is an enlarged sectional view of a discharge valve assembly in accordance with another prior art. Figure 3 is a longitudinal sectional view of a slant plate type refrigerant compressor in accordance with the present invention. Figure 4 is an enlarged sectional view of a discharge valve assembly in accordance with a first embodiment of the present invention. Figure 5 is a cross sectional view of the discharge valve assembly taken along line 5-5 of Figure 3. Figure 6 is graphical illustration of the relationship between pressure in cylinder bore and time T, in accordance with a first embodiment of the present invention. Figure 7 is graphical illustration of the relationship between magnitude of noise of the compressor and rotation speed of the compressor, in accordance with a first embodiment of the present invention. Figure 8 is an enlarged sectional view of a discharge valve assembly in accordance with a second embodiment of the present invention. Figure 9 is an enlarged sectional view of a discharge valve assembly in accordance with a third embodiment of the present invention. With reference to Figure 3, a fluid displacement apparatus in accordance with the present in shown. The fluid apparatus is described in terms of a piston type compressor, but it will be readily appreciated by those skilled in the art that the invention could be adapted to other fluid displacement apparatus. A compressor comprises cylindrical housing assembly 20 including cylinder block 21, crank chamber 22, front end plate 23, rear end plate 24, and valve plate 25. Crank chamber 22 is formed between cylinder block 21 and front end plate 23. Front end plate 23 is mounted on one end of cylinder block 21 formed ( to the left side in Figure 1 ) by a plurality of bolts ( not shown ). Rear end plate 24 is mounted on the opposite end of cylinder block 21 by a plurality of bolts (not shown ). Valve plate 25 is located between rear end plate 24 and cylinder block 21. Opening 231 is centrally formed in front end plate 23 and supports drive shaft 26 by bearing 30 disposed in the opening. The inner end portion of drive shaft 26 is rotatable supported by bearing 31 disposed within center bore 210 of cylinder block 21. Bore 210 extends to a rearward end surface of cylinder block 21 wherein there is disposed valve control mechanism. Cam rotor 40 is fixed on drive shaft 26 by pin member 261 and rotates with drive shaft 26. Thrust needle bearing 32 is disposed between the inner end surface of front end plate 23 and the adjacent axial end surface of cam rotor 40. Cam rotor 40 includes arm 41 having pin member 42 extending therefrom. Slant plate 50 is adjacent cam rotor 40 and includes opening 53 through which passes drive shaft 26. Slant plate 50 includes arm 51 having slot 52. Cam rotor 40 and slant plate 50 are connected by pin member 42, which is inserted in slot 52 to create a hinged joint. Pin member 42 is slid able within slot 52 to allow adjustment of the angular position of slant plate 50 with respect to the longitudinal axis of drive shaft 26. Wobble plate 60 is nutatably mounted on slant plate 50 through bearings 61 and 62. Fork-shaped slider 63 is attached to the outer peripheral end of wobble plate 60 and is slidably mounted about sliding rail 64 held between front end plate 23 and cylinder block 21. Fork-shaped slider 63 prevents rotation of wobble plate 60, and wobble plate 60 nutates along rail 64 when cam rotor 40 rotates. Cylinder block 21 includes a plurality of peripherally located cylinder chambers 70 in which pistons 72 reciprocate. Each piston 72 is connected to wobble plate 60 by a corresponding connecting rod 73. Each piston 72 and connecting rod 73 substantially compose piston assembly 71 as discussed below. Rear end plate 24 includes peripherally located annular suction chamber 142 and centrally located discharge chamber 152. Valve plate 25 is located between cylinder block 21 and rear end plate 24 and includes a plurality of valved suction holes 242 linking each suction chamber 142 with respective cylinders 70. Valve plate 25 also includes a plurality of valved discharge holes 252 linking discharge chamber 152 with cylinder chambers 70. Each suction chamber 142 includes an inlet port which is connected to an evaporator of the external cooling circuit( not shown). Discharge chamber 152 is provided with outlet portion connected to a condenser of the cooling circuit ( not shown ). Gaskets 27 and 28 are located between cylinder block 21 and the inner surface of valve plate 25, and the outer surface of valve plate 25 and rear end plate 24, respectively, to seal the mating surfaces of cylinder block 21, valve plate 25 and rear end plate 24. Disk-shaped adjusting screw member 33 is disposed in a central region of bore 210 located between the inner end portion of drive shaft 26 and valve control mechanism. Disk-shaped adjusting screw member 33 is screwed into bore 210 to be in contact with the inner end surface of drive shaft 26 through washer, and adjusts an axial position of drive shaft 26 by tightening and loosing thereof. Piston assembly 71 includes connecting rod 73 which includes a pair of ball portions 73a and 73b formed at both ends thereof and cylindrically-shaped piston 72 which is connected to ball portion 73b formed at the rear end of connecting rod 73. Referring to Figure 4 and 5, the discharge valve assembly includes discharge reed valve 81 and valve retainer 180 which are secured together to valve plate 25 by fixing bolts 82. Discharge reed valve 81, which is made of an elastic member e.g., thin spring steel, regulates the flow of the refrigerant gas. Discharge reed valve 81 has a substantially flat portion 81a formed to the side of bolt 82 and sealing portion 81b extending from portion 81a. Valve plate 25 includes recessed portion 250 formed so that its depth increases with radial distance from point C, which is spaced by a distance L1 from fixing bolt 82. Recessed portion 250 includes curved surface 251e surrounding discharge hole 252. When discharge reed valve 81 is in its closed position, it sealingly engages inclined or curved surface 251 has a curved cross section passing on point C and having a radius of curvature R3. The curved cross section defines the maximum amplitude of natural vibration when discharge reed valve 81 vibrates with fixing point C as the fulcrum as shown by the phantom representation of discharge reed valve 81. In other word, the natural vibration shape of discharge reed valve 81 approximates a curve having radius of curvature R3. Recessed portion 250 includes end wall 254 extending from inclined surface 251. End wall is preferred parallel outside edge 81c of discharge reed valve 81 when seated against inclined surface 251. A gap is created between end wall 254 of valve plate 25 and edge 81c of discharge reed valve 81. Further, valve plate 25 includes discharge hole 252 extending therethrough. Recessed portion 250 and the portions therein, i.e., inclined surface 251, end surface 25a, and front end 253 of inclined surface 251 collectively comprise a valve seat. Further, valve retainer 180 includes two surface portions, the flat surface portion 180a and curved surface portion 180b. At point D, which is spaced a distance L2 from bolt 82. Curved surface 180b has a curved cross section passing on point D and having a radius of curvature R4. The curved cross defines the maximum amplitude of natural vibration when discharge reed valve 81 vibrates with fixing point D as the fulcrum. In other word, the natural vibration shape of discharge reed valve 81 approximates a curve having a radius of curvature R4. Further, valve retainer 180 is preferably made of an resin or engineering plastic e.g., polyacetal resin. Valve retainer 180 limits the bending movement of discharge reed valve 81 in the direction which the refrigerant gas exits discharge hole 252. Discharge reed valve 81 bends as it opens and close discharge hole 252, and has a spring constant which allows discharge reed valve 81 to block discharge hole 252 until the pressure in compression chamber 70 reaches a predetermined value. The relation ships of L, L1 and L2 is such that L1 < L < L2. During operation of the fluid displacement apparatus, drive shaft 26 is rotated by the engine of the vehicle through electromagnetic clutch 300. Cam rotor 40 is driven with drive shaft 26, which rotates slant plate 50 as well, which in turn causes wobble plate 60 to nutate. Nutational motion of wobble plate 60 reciprocates pistons 72 in their respective cylinders 70. As pistons 72 are reciprocated, refrigerant gas, which is introduced into suction chamber 142 through inlet portion ports, and is then compressed. The compressed refrigerant gas is discharged to discharge chamber 152 from each cylinder 70 through discharge holes 252, and therefrom into the cooling circuit through outlet portion. The impact force with which discharge reed valve 81 strikes retainer 180 is smaller than that of which discharge reed valve 81 strikes retainer 80 in the arrangement of Figure 1 and 2. This is due to the realization that discharge reed valve 81 more readily resists bending toward retainer 180 in the case of Figure 4, whereas discharge reed valve 81 in the configuration of Figure 1 and 2 more readily bends toward retainer 80. The magnitude of flexual rigidity of discharge reed valve 81, which is shaped as a leaf spring, is generally in inverse proportional to the distance from the fulcrum point. Distance L2 of Figure 4 is greater than distance L in Figure 2. The flexual rigidity, which discharge reed valve 81 has when bending toward retainer 180 with fixing point D as the fulcrum, is smaller than that with point A as the fulcrum as in Figure 2 (or Figure 1). As a consequence, noise and vibration caused by discharge reed valve 81 striking retainer 180 and discharge reed valve 81 quickly returns to its inclined surface 251 at the beginning of suction stage. This improvement further provides a discharge reed valve which reliably closes the discharge hole during suction stage. Figure 8 illustrates a second preferred embodiment of the present invention. Elements in Figure 8 similar to those in Figure 4 are designated with the same reference numerals. Valve plate 25 includes recessed portion 250 whose depth increases with distance from point C, which is located on valve plate 25 and spaced a distance L1 from fixing bolt 82. Recessed portion 250 includes curved surface 351 surrounding discharge hole 252. When discharge reed valve 81 is in its closed position, it sealingly contacts curved surface 351. Inclined surface 351 has a curved cross section comprising four curve segments having radius of curvatures R3, R5, R6 and R7. First curve segment starts at point C and terminate at point E. A line M is drawn perpendicular to end surface 25a of valve plate 25 and intersecting point C. The first curve segment crosses a line N, which is drawn in parallel to a line M at point E. Second curve segment starts at point E and terminate at point F. The second segment curve also crosses a line P, which is drawn in parallel to line M, at point F. Third curve segment starts at point F and terminate at point G. The third segment curve also crosses line Q, which is drawn in parallel to a line M, at point G. Fourth curve segment starts at point G and terminate at point H. The fourth segment curve also crosses a line S, which is parallel to line M, at point H. Line N, P, Q divide the distance between line M and lines into quarters. Radius of curvature R3 approximates to the natural vibration shape of discharge reed valve 81. The relation ships of R3, R5, R6 and R7 is such that R7 < R6 < R5 < R3. A slightly air gap is created between the curved cross section and the curve shape of reed valve 81 at its the maximum amplitude when naturally vibrating with fixing point C as the fulcrum as shown in phantom in Figure 8. In such structure, substantially the same advantages as those in the first preferred embodiment are realized. Moreover, discharge reed valve 81 of this embodiment closes discharge hole 252 with the impact force smaller than that of Figure 4 ( having only one radius of curvature R3 )since discharge reed valve 81 is constantly subjected to the restoring force of valve member toward opening direction when each portion of discharge reed valve 81 bends and endlessly close to inclined surface 351. Figure 9 illustrates a second preferred embodiment of the present invention. Elements in Figure 9 similar to those in Figure 4 are designated with the same reference numerals. Instead of a curved cross section, flat surface 451 has a linear line cross section starting at point C and terminating at point H. A slightly air gap is created between the linear cross section and the curve shape assumed by reed valve 81 at its the maximum amplitude, when vibrating in natural frequency with fixing point C as the fulcrum as shown in phantom. Substantially, the same advantages as those in the first preferred embodiment are realized. Figure 6 and 7 illustrate the relationship between the apparatus of the preferred embodiment and that of Figure 2. Figure 6 depicts the pressure in cylinder bore versus time T. The preferred embodiment are shown to reduce the delay of closing of discharge reed valve 81. Further, Figure 7 shows the magnitude of noise caused by the compressor versus the rotation speed of the compressor. The preferred embodiment reduce noise level of the compressor in comparison with the noise generated by the compressor of Figure 2. Although the present invention has been described in connection with the preferred embodiment, the invention is not limited thereto. It will be easily understood by those of ordinary skill in the art that variations and modifications can be easily made within the scope of this invention as defined by the appended claims. Thus, while the preferred embodiments illustrates the invention in a particular type fluid displacement apparatus, i.e., a slant plate type compressor, the invention can be used in any other type of fluid displacement apparatus, such as a scroll type displacement apparatus.

Claims: A fluid displacement apparatus comprising: a housing (20) including a front end plate (23) and a rear end plate (24); a valve plate member (25) disposed in the housing and dividing the housing into a first chamber (22) and a second chamber (152), the second chamber comprising a discharge chamber; a passage (252) formed in the valve plate member extending between the first chamber and the discharge chamber, the passage having an open end through which discharge fluid flows; an elastic valve member (81) disposed on the valve plate, the valve member having a spring constant causing the passage to remain blocked until the pressure in the first chamber reaches a predetermined value; a valve retainer member (180) secured by a securing member (82) to the valve plate, the valve retainer member bent away from the valve plate, the valve retainer member limiting bending movement of the valve member, and a valve seat (25a,251,253) formed on the valve plate around the open end of the passage, the valve seat comprising a recess (250) formed in the valve plate, the recess including a surface (251) inclined with increasing depth in radial direction of the valve plate, characterised by the inclined surface (251) beginning at a point radially outside the securing member (82) and the point at which the valve retainer member is bent being radially outside the point where the inclined surface begins. An apparatus according to claim 1, wherein the inclined surface (251) of the recess (250) includes a curved cross section comprising at least one radius of curvature. An apparatus according to claim 2, wherein the at least one radius of curvature of the curved cross section approximates to the maximum amplitude of natural vibration of the elastic valve member (81). An apparatus according to claim 1, wherein the inclined surface (251) of the recess (250) includes a curved cross section comprising a plurality of curves which have varying radii of curvature, the radii of curvature being, with increased radial distance from the securing member (82), successively smaller than the adjacent preceding curve. An apparatus according to claim 1, wherein the inclined surface (251) of the recess (250) includes a linear cross section. An apparatus according to any one of the preceding claims, wherein an air gap is created between the inclined surface (251) of recess (250) and the elastic valve member (81) when the elastic valve member reaches maximum amplitude in natural vibration. An apparatus according to any one of the preceding claims, wherein the surface of the retainer member (180) which faces the elastic valve member (81) comprises a curved cross section having at least one radius of curvature. An apparatus according to claim 7, wherein the at least one radius of curvature approximates to the maximum amplitude in natural vibration of the elastic valve member (81). An apparatus according to any one of the preceding claims, wherein the retainer member (180) comprises engineering plastic.

Inventors: HASHIMOTO KENJI, MATSUMURA YOSHITO, HASHIMOTO, KENJI, MATSUMURA, YOSHITO
Applicants: SANDEN CORP, SANDEN CORPORATION
Application year: 1995
Main classification: F04B39
IPC codes: F16F9, F04B39