WOBBLE PLATE TYPE COMPRESSOR WITH VARIABLE DISPLACEMENT MECHANISM

Abstract: A refrigerant compressor (10) including a compressor housing (20) having a cylinder block (21) is disclosed. A plurality of cylinders (70) are formed around the periphery of the cylinder block (21) and a piston (71) is slidably fitted within each of the cylinders (70) and is reciprocated by a drive mechanism. A crank chamber (22) is formed between the cylinder block (21) and a front end plate (23) of the compressor housing (20). The drive mechanism includes a drive shaft (26), a rotor (40) disposed on said drive shaft (20), a slant plate with an adjustable slant angle disposed adjacent to the rotor (40), and a wobble plate (60) disposed adjacent to the slant plate. The drive shaft (26) is ro­ tatably supported within the front end plate (23). Rotation of the drive shaft (26) causes rotation of the rotor (40) and the slant plate, causing nutational motion of the wobble plate (60) to reciprocate the pistons (71) within their cylinders (70). The compressor housing (20) includes a rear end plate (24) incuding suction and discharge chambers (241, 251). An inlet portion (241a) of the suction chamber (241) and an outlet portion (251a) of the discharge chamber (251) link the compressor (10) with an external fluid circuit. The inlet portion (241a) is linked to an external evaporator. A narrowed portion (243) is located between the inlet portion (241a) of the suction chamber (241) and a main portion (241b) of the suction chamber (241) and creates a pressure dif­ ference therebetween. A communication path (92) links the crank chamber (22) and the suction chamber (241) and is con­ trolled by a valve control means (85, 85b). When the capacity of the compressor (10) is changed, the valve control means (85, 85b) links the crank chamber (22) with the external evaporator via the inlet portion (241a) due to the pressure difference created by the narrowed portion (243) to reduce the outlet pressure thereof, preventing a decrease in efficiency of the evaporator.

Description: The present invention relates to a refrigerant compressor, and more particularly, to a wobble plate type compressor with a variable displacement mechanism suitable for use in an automotive air conditioning system. It has been recognized that it is desirable to provide a wobble plate type piston compressor with a displacement or capacity adjusting mechanism to control the compression ratio in response to demand. As disclosed in U.S. Patent No. 4,428,718, the compression ratio may be controlled by changing the slant angle of the sloping surface of a slant plate in response to operation of a valve control mechanism. The slant angle of the slant plate is adjusted to maintain a constant suction pressure in response to a change in the heat load of the evaporator of an external circuit including the compressor or a change in rotation speed of the compressor. In an air conditioning system, a pipe member connects the outlet of an evaporator to the suction chamber of the compressor. Accordingly, a pressure loss occurs between the suction chamber and the outlet of the evaporator which is directly proportional to the "suction flow rate" therebetween as shown in Figure 5. As a result, as shown by the dash line in Figure 4, when the capacity of the compressor is adjusted to maintain a constant suction chamber pressure in response to a change in the heat load of the evaporator or the rotation speed of the compressor, the pressure at the evaporator outlet increases as well. This increase in the evaporator outlet pressure results in an undesirable decrease in the heat exchanging ability of the evaporator. U.S. Patent 4,428,718 is acknowledged in the preamble of claim 1. It discloses a valve control mechanism to aliminate this problem. The valve control mechanism includes a device which senses the discharge pressure of the compressor and in response thereto, the valve element is shifted to maintain a constant pressure at the evaporator outlet portion. That is, the valve control mechanism makes use of the fact that the discharge pressure of the compressor is roughly directly proportional to the suction flow rate. However, the relationship between the discharge pressure and the suction flow rate is not constant in every air conditioning system. Furthermore, the discharge pressure varies greatly in response to the velocity of air passing through the condensor. Accordingly, in an automotive air conditioning system in which the wind velocity varies greatly in response to the speed of the vehicle, the relationship is indefinite and unreliable. Therefore, the system is not sufficiently effective in preventing the undesirable increase in pressure at the evaporator outlet. It is an object of this invention to provide a wobble plate type piston compressor with a capacity adjusting mechanism which compensates for the increase in pressure at the evaporator outlet when the capacity of the compressor is adjusted, to maintain a constant evaporator outlet pressure. This problem is solved by the refrigerant compressor indicated in claim 1. The valve shifting element may include a piston attached to the valve element. The valve element may include a bellows and a valve member. The pressure difference produced by the narrowed portion causes the valve shifting element to shift the valve element, linking the crank member with the inlet portion of the suction chamber to maintain a constant pressure at the outlet of the evaporator when the suction flow rate changes. Further objects, features and other aspects of the invention will be understood from the detailed description of the preferred embodiments of this invention with reference to the drawings. Figure 1 is a vertical longitudinal sectional view of a wobble plate type refrigerant compressor in accordance with a first embodiment of this invention. Figure 2 is a vertical longitudinal sectional view of a wobble plate type refrigerant compressor in accordance with a second embodiment of this invention. Figure 3 is a graph showing the relation between the pressure of the suction chamber and the suction flow rate, wherein, the dash line represents the prior art and the solid line represents the present invention. Figure 4 is a graph showing the relation between the pressure at the outlet of an evaporator and the suction flow rate, wherein, the dash line shows the prior art and the solid line shows the present invention. Figure 5 is a graph showing the relation between the pressure loss occurring between the outlet of the evaporator and the compressor and the suction flow rate. With reference to Figure 1, wobble plate type refrigerant compressor 10 in accordance with one embodiment of the present invention is shown. Compressor 10 includes cylindrical housing assembly 20 including cylinder block 21, front end plate 23 at one end of cylinder block 21, crank chamber 22 formed between cylinder block 21 and front end plate 28, and rear end plate 24 attached to the other end of cylinder block 21. Front end plate 23 is mounted on cylinder block 21 forward (to the left in Figure 1) of crank chamber 22 by a plurality of bolts 101. Rear end plate 24 is mounted on cylinder block 21 at its opposite end by a plurality of bolts 102. Valve plate 25 is located between rear end plate 24 and cylinder block 21. Opening 231 is centrally formed in front end plate 23 for supporting drive shaft 26 therethrough by bearing 30 disposed within. The inner end portion of drive shaft 26 is rotatably supported by bearing 31 disposed within central bore 210 of cylinder block 21. Bore 210 has an increased diameter portion rearward (to the right) of the end of drive shaft 26 containing the valve control mechanism as discussed below. Cam rotor 40 is fixed on drive shaft 26 by pin member 261 and rotates therewith. 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 to 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 slidable 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 rotatably 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 on 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 71 reciprocate. Each piston 71 is connected to wobble plate 60 by a corresponding connecting rod 72. Rear end plate 24 includes peripherally located annular suction chamber 241 and centrally located discharge chamber 251. Valve plate 25 is located between cylinder block 21 and rear end plate 24 and includes a plurality of valved suction ports 242 linking suction chamber 241 with respective cylinders 70. Valve plate 25 also includes a plurality of valved discharged ports 252 linking discharge chamber 251 with respective cylinders 70. Suction ports 242 and discharge ports 252 are provided with suitable reed valves as described in U.S. Patent No. 4,011,029 to Shimizu. Suction chamber 241 includes inlet portion 241a which is connected to an evaporator of the external cooling circuit (not shown). Inlet portion 241a is linked to main portion 241b of suction chamber 241 via narrowed passage 243. Discharge chamber 251 is provided with outlet portion 251a connected to a condensor 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. The valve control mechanism includes cup-shaped casing 80 disposed within central bore 210 rearward to the end of drive shaft 26. Cup-shaped casing 80 may be disposed in a region of central bore 210 with an extended diameter. At its open end, cup-shaped casing 80 is bent inward and is disposed adjacent to valve plate 25. A pair of O-ring seals 81 are disposed between an inner peripheral surface of central bore 210 and an outer peripheral surface of cup-shaped casing 80. Seat member 82 is disposed on the inner surface of bent open end 83 of casing 80 to define chamber 84 between seat member 82 and cup-shaped casing 80. Seat member 82 includes annular projection 82a extending into chamber 84 and having a threaded interior. Gas charged bellows 85 has a predetermined internal pressure and is disposed within chamber 84. Screw member 85a is attached at the rear end of bellows 85 and is screwed into annular projection 82a to secure bellows 85 to seat members 82. Valve member 85b is located at the other end of bellows 85. Generally cup-shaped piston member 86 is disposed within chamber 84 and valve member 85b extends through its closed bottom surface. Piston member 86 is attached to the valve element including both valve member 85b and bellows 85. Cup-shaped piston member 86 includes side wall 87 extending from its open end to a mid-point approximately half way there along. Side wall 87 is adjacent to an inner surface of cup-shaped casing 80 up to its approximate midpoint and then bends inward to form reduced diameter portion 87b. Cup-shaped piston member 86 divides chamber 84 into front chamber 84a located between portion 87b and cup-shaped casing 80, and rear chamber 84b located between piston member 86 and seat member 82. A diaphragm may also be used in place of cup-shaped piston member 86. Hole 90 is formed approximately at the center of the bottom of cup-shaped casing 80 and links crank chamber 22 with front chamber 86a. Valve member 85b fits within hole 90 to control this link. Hole 91 is formed in the lower side wall of cup-shaped casing 80 at a location adjacent to front chamber 84a forward of piston member 86. Conduit 92 is formed within cylinder block 21 and links front chamber 84a with inlet portion 241a of suction chamber 241 via hole 91 in casing 80, hole 96 in valve plate 25, and corresponding conduit 92a formed in rear end plate 24. Hole 93 is formed in seat member 82 and links rear chamber 84b to main portion 241b of suction chamber 241 via conduit 94 formed between cylinder block 21 and valve plate 25, and hole 94a formed through valve plate 25. During operation of compressor 10, drive shaft 26 is rotated by the engine of the vehicle through an electromagnetic clutch (not shown). Cam rotor 40 is rotated with drive shaft 26, rotating slant plate 50 as well which causes wobble plate 60 to nutate. Nutational motion of wobble plate 60 reciprocates pistons 71 in their respective cylinders 70. As pistons 71 are reciprocated, refrigerant gas which is introduced into main portion 241b of suction chamber 241 through inlet 241a and narrowed passage 243 is drawn into each cylinder 70 through suction ports 242 and then compressed. The compressed refrigerant gas is discharged to discharge chamber 251 from each cylinder 70 through discharge ports 252, and therefrom into the cooling circuit through outlet portion 251a. The capacity of compressor 10 is adjusted to maintain a constant pressure in suction chamber 241 in response to a change in the heat load of the evaporator or a change in the rotating speed of the compressor. The capacity of the compressor is adjusted by changing the angle of the slant plate which is dependent upon the crank chamber pressure. An increase in crank chamber pressure decreases the slant angle of the slant plate and thus the wobble plate, decreasing the capacity of the compressor. A decrease in the crank chamber pressure increases the angle of the slant plate and the wobble plate and thus increases the capacity of the compressor. With reference to Figures 3 and 4, the effect of the valve control mechanism of the present invention in maintaining a constant pressure at the outlet of the evaporator during capacity control of the compressor will be explained. When the refrigerant gas flowing from the evaporator flows from inlet portion 241a to main portion 241b of suction chamber 241 through narrowed passage 243, a pressure loss (ΔP) occurs due to the effect of narrowed passage 243. Specifically, the pressure at inlet portion 241a is (P), and the pressure in main portion 241b is (P-ΔP). Accordingly, the pressure in front chamber 84a which is linked directly to inlet portion 241a through conduits 92 and 92a is greater than the pressure in rear chamber 84b which is linked to main portion 241b by conduit 94 by (ΔP). If the inner diameter of chamber 84 is represented by (D), a force (F) which is equal to (Δ P·π D 4 ²) acts on cup-shaped piston member 86 causing it to move towards the right in Figure 1. As can be seen from this formula, the rightward force F is directly proportional to the pressure loss (ΔP). Additionally, the pressure loss (ΔP) is directly proportional to the suction flow rate. Thus the rightward acting force F acting on cup-shaped piston member 86 is dependent upon the suction flow rate, causing bellows 85 to contact moving valve member 85b to the right and out of hole 90 to link crank chamber 22 with inlet portion 241a to lower the pressure therein. The movement of valve member 85b is dependent on the suction flow rate and occurs when the rate increases. As a result, the increase in evaporator outlet pressure caused by an increase in suction flow rate is compensated by a decrease in pressure in inlet portion 241a due to the action of the valve control mechanism of the present invention. As shown in Figure 4, the pressure at the evaporator outlet is maintained constant as the suction flow increases during a change in compressor capacity. It should be noted that the increase in the leftward acting force of bellows 85 caused by a decrease in pressure (ΔP) in chamber 84b may be substantially disregarded because the longitudinal pressure receiving area of cup-shaped piston member 86 which extends throughout the diameter of cup-shaped housing 80 is much greater than the leftward acting restoring force of bellows 85. Figure 2 shows a second embodiment of the present invention in which the same numerals are used to denote the same elements shown in Figure 1. In the second embodiment, the valve control mechanism includes bellows 285 which longitudinally contracts or expands in response to the pressure of crank chamber 22. Bellows 285 is disposed within chamber 840 defined between cup-shaped casing 800 and valve plate 25. Wall 861 extends within cup-shaped casing 800 and divides chamber 840 into first chamber 841 on the forward side and second chamber 842 on the rearward side as shown in Figure 2. Wall 861 includes hole 890 centrally located therethrough. Screw member 285a is attached at the forward side of bellows 285 and is screwed into threaded portion 801 formed at the center of the bottom end of cup-shaped casing 800. Valve member 285b is attached at the opposite end of bellows 285 and fits within hole 890. Diaphragm 886 having pin 887 disposed thereon is located within second chamber 842 and further divides second chamber 842 into front second chamber 842a and rear second chamber 842b. Pin 887 projects from diaphragm 886 and is disposed adjacent to valve member 285b through hole 880. A pair of holes 891 is formed at the bottom and (left side) of cup-shaped casing 800 to link crank chamber 22 with first chamber 841 through a gap in bearing 31 supporting drive shaft 20. Hole 892 is formed in the side wall of cup-shaped casing 800 adjacent to front second chamber 842, that is, to the right of wall 861. Hole 894 is formed in the side wall of cup-shaped housing 800 at a location adjacent to rear second chamber 842b, that is, to the right of diaphragm 886. Conduit 893 is formed in cylinder block 21 and links front second chamber 842a to main portion 241b via hole 892 and hole 897 in rear end plate 24. Conduit 895 is formed in rear end plate 24 and links inlet portion 241a and rear second chamber 842b through hole 894 in cup-shaped housing 800 and hole 896 in rear end plate 24. As in the first embodiment, a pressure difference is created between inlet portion 241a and main portion 241b of suction chamber 241 by narrowed region 243. However, this pressure difference creates a leftward force on diaphragm 886 which moves pin 887 to the left, forcing valve element 285b out of hole 890 and thereby linking crank chamber 22 to the evaporator. The operation of the valve control mechanism of this embodiment is substantially similar to that in the first embodiment and a further explanation of this operation is omitted. This invention has been described in detail in connection with the preferred embodiments. These embodiments, however, are merely for example only and the invention is not restricted thereto. It will be understood by those skilled in the art that other variations and modifications can easily be made within the scope of this invention as defined by the claims.

Claims: A refrigerant compressor (10) including a compressor housing (20) having a cylinder block (21) provided with a plurality of cylinders (70), a front end plate (23) disposed on one end of said cylinder block (21) and enclosing a crank chamber (22) within said cylinder block (21), a piston (71) slidably fitted within each of said cylinders (70) and reciprocated by a drive mechanism including a wobble plate (60), a rotor (40) connected to a drive shaft (26), an adjustable slant plate (50) having an inclined surface in close proximity to said wobble plate (60) adjustably connected to said rotor (40) and having an adjustable slant angle, said slant angle changing in response to a change in pressure in said crank chamber (22) to change the capacity of said compressor (10), said front end plate (23) rotatably supporting said drive shaft (26) in a hole (231) therethrough, a rear end plate (24) disposed on the opposite end of said cylinder block (21) from said front end plate (23) and defining a suction chamber (241) and a discharge chamber (251) therein, said suction and discharge chambers (241, 251) having inlet and outlet portions (241a, 251a) respectively linked to an external fluid circuit, a communication path (90, 92) linking said crank chamber (22) with said suction chamber (241) or inlet portion (241a), and a valve control means controlling the opening and closing of said communication path (92), said valve control means including a valve element (85, 85b) opening and closing said communication path (90, 92), characterized by a valve shifting element (86) responsive to the pressure difference on either side thereof, and a narrowed passage (243) formed between said inlet portion (241a) of said suction chamber (241) and a main portion (241b) of said suction chamber (241) for producing the pressure difference to shift said valve element (85b) from a position closing said communication path (90, 92) to a position opening said communication path (90, 92). The refrigerant compressor (10) of claim 1, characterized in that said valve element (85, 85b) is shifted by said valve motion shifting element (86) to open said communication path (90, 92) when said pressure difference increases. The refrigerant compressor (10) of claim 1, characterized in that said inlet portion (241a) is linked by a conduit (92a) to said crank chamber (22), said conduit (92a) bypassing said narrowed portion (243). The refrigerant compressor (10) of one of claims 1 to 3, characterized in that said valve element (85, 85b) includes a bellows (85) and a valve member (85b), said bellows (85) longitudinally contracting or expanding in response to the pressure of said suction chamber (241). The refrigerant compressor (10) of one of claims 1 to 4, characterized in that said valve shifting element is a cup-shaped piston member (86). The refrigerant compressor (10) of claim 5, characterized in that said cylinder block (21) includes a central bore (210) containing a cup-shaped casing (80) therein and a cup-shaped piston member (86) separating the interior of said cup-shaped casing (80) into a first and a second interior chamber (84a, 84b), said first chamber (84a) being linked to said crank chamber (22) via a hole (90) in said cup-shaped casing (80), said second chamber (84b) being linked to said main portion (241b) of said suction chamber (241). The refrigerant compressor (10) of claim 6, characterized in that said valve element (85, 85b) includes a bellows (85) and a valve member (85b) attached to said piston member (86), said bellows (85) being located in said second chamber (84b) and said valve member (85b) adjacent to and fitting through said hole (90) in said cup-shaped casing (80), said main portion (241b) of said suction chamber (241) being linked to said second chamber (84b), and said inlet portion (241a) being linked to said first chamber (84a) via a conduit (92) bypassing said narrowed portion (243), wherein said pressure difference created by said narrowed portion (243) is applied to said piston element (86) to move said valve member (85b) to open said hole (90) in said cup-shaped casing (80) to link said crank chamber (22) with said inlet portion (241a) of said suction chamber (241). The refrigerant compressor (10) of one of claims 1 to 7, characterized in that said valve element (85, 85b) includes a bellows (85) and a valve member (85b), said bellows (85) longitudinally contracting or expanding in response to the pressure of said suction chamber (22). The refrigerant compressor (10) of one of claims 1 to 8, characterized in that said valve motion shifting element (86) is a diaphragm.

Inventors: TERUACHI, KIYOSHI
Applicants: SANDEN CORPORATION
Application year: 1988
Main classification: F04B27
IPC codes: F04B27