Oil pump apparatus

Abstract: An oil pump for a motor vehicle compromises an oil pump housing (22); a rotor assembly (26,36) located in the oil pump housing (22), the rotor assembly (26,36) defining a first set of pockets (40g to 40k) having a capacity increasing in the rotating direction of the rotor assembly and a second set of pockets (40b to 40f) having a capacity deceasing in the rotating direction of the rotor assembly; a plurality of suction ports (44,46) connected with the first set of pockets (40g to 40k), each of the suction ports (44,46) being isolated from the or each adjacent suction port; a discharge port (42) connected with the second set of pockets (40b to 40f); and a control valve (64,92 or 104) for selectively controlling the delivery of hydraulic oil to be pumped to the suction ports (44,46).

Description: Field of the Invention The present invention relates to an oil pump for a vehicle, and especially to a pump which produces an output pressure which rises with the rotational speed of a drive source, for example a crank shaft of an internal combustion engine. Background of the Invention A conventional pump includes a suction port, a discharge port, a rotor and a drive source which makes the rotor rotate. When the rate of rotation of the rotor is increased, the amount of oil discharged from the discharge port is increased so that the output pressure increases. Therefore it happens at times that the oil pump discharges more oil than is necessary. Such an oil pump is disclosed in, for example, Japanese Utility Model Patent laid-open Application No.61(1986)-23485 which describes an oil pump apparatus which has a drive source and two gear pumps in one body. When the drive source rotates at low speed, the oil pump apparatus drives two gear pumps to obtain the necessary amount of the oil. When the drive source rotates at high speed, the oil pump apparatus drives only one of the two gear pumps so that the oil pump is able to avoid discharging more than the necessary amount of the oil, and thereby working efficiency is improved. However, the above oil pump needs two gear pumps, and is not therefore very compact and is sometimes too bulky to be mounted on the vehicle body. In addition, there is known an oil pump which has a relief valve 200 as shown in Fig. 13. Such an oil pump includes a pump body 202, a rotor 204 and the relief valve 200. The pump body 202 has a suction port 206 and a discharge port 208. The rotor 204 has a plurality of teeth located in a pumping chamber 210 of the pump body 202. The relief valve 200 is operated, corresponding to the pressure at the discharge port 208. When the speed of the rotor 204 is increased until the pressure at the discharge port 208 reaches at a predetermined pressure (P1), the relief valve 200 opens against the bias of a spring, and excess oil under pressure is discharged from a relief port of the relief valve 200. However such an oil pump must be capable of generating an output in excess of the predetermined pressure (P1) so that the oil pump is designed to be over-rated and is therefore inefficient. Drawings Fig. 1 is a diagrammatic illustration of a first embodiment of an oil pump of the invention operating at a low input speed; Fig. 2 is a diagrammatic illustration of the oil pump of Fig 1, operating at a mid-range input speed; Fig. 3 is a diagrammatic illustration of the oil pump apparatus of Fig. 1, operating at a high input speed; Fig. 4 is an axial section through a valve of the oil pump of Figs 1 to 3, as the input speed rises from low speed to middle speed; Fig. 5 is a graph illustrating the characteristic of outlet-amount plotted against input speed of an oil pump in accordance with the invention; Fig. 6 is a diagrammatic illustration, similar to Fig. 1 of a second embodiment of an oil pump in accordance with the invention; Fig. 7 is a section through a valve of the second embodiment when the rotor rotates in lower middle speed; Fig. 8 is a section through the valve of the second embodiment when the rotor rotates in upper middle speed; Fig. 9 is a section through a valve of the second embodiment when the rotor rotates in high speed; Fig. 10 is a diagrammatic illustration, similar to Fig. 1 of a third embodiment of an oil pump in accordance with the invention; Fig. 11 is a diagrammatic illustration, similar to Fig. 1 of a fourth embodiment of an oil pump in accordance with the invention; Fig. 12 is an enlarged view of part of the oil pump of Fig. 11, and Fig. 13 is a diagrammatic illustration of an oil pump according to the prior art. Detailed Description of the Preferred Embodiments Referring first to Fig. 1, there is shown a first preferred embodiment of an oil pump 20 of the invention. The oil pump 20 is designed to be mounted on a vehicle and it is actuated by a crankshaft of an internal combustion engine. The oil pump 20 is provided with an oil pump housing 22 which is made of metal, such as an aluminium-based alloy or an iron-based alloy. In the oil pump housing 22 is formed a pump chamber 24, housing an outer rotor 26 which is provided with a plurality of internal gear teeth 28 so as to constitute a driven gear. Furthermore, an inner rotor 30 is disposed in the pump chamber 24 and is located inside the outer rotor 26. The axes of the outer rotor 26 and of the inner rotor 30 are spaced apart by a predetermined distance. The inner rotor 30 is connected to the crank shaft 32 of the internal combustion engine, and it is rotated together with the crank shaft 32. In general, the inner rotor 30 is designed to rotate at a revolving speed of from 600 to 7000 rpm. On an outer periphery of the inner rotor 30 there is formed a plurality of external gear teeth 34 so as to constitute a drive gear. The internal gear teeth 28 and the external gear teeth 34 are designed to be a trochoid curve or a cycloid curve. When the inner rotor 30 is rotated in the direction of the arrow 36 of Fig. 1, the external gear teeth 34 of the inner rotor 30 engage with the internal gear teeth 28 of the outer rotor 26 one after another, accordingly the outer rotor 26 is rotated in the same direction. Between the internal gear teeth 28 and the external gear teeth 34, there are formed eleven pockets 40a through 40k as shown in Fig. 1. In Fig. 1, the pocket 40a has the largest volume and the pocket 40f has the smallest volume. The pockets 40g to 40k, disposed upstream with respect to the pocket 40a, produce an inlet pressure, because their volume enlarges as the inner rotor 30 is rotated, and they act to draw the hydraulic oil. The pockets 40b to 40f, disposed downstream with respect to the pocket 40a, produce an outlet pressure, because their volume diminishes as the inner rotor 30 is rotated, and they act to discharge the hydraulic oil. In the oil pump housing 22 there is formed a discharge port 42 which is connected to the pockets 40b to 40f, and is adapted to discharge the hydraulic oil out of the pump chamber 24 as the inner rotor 30 is rotated. In the oil pump housing 22, two suction ports 44 and 46 are formed. The suction port 44 is connected to the pockets 40g to 40i and the suction port 46 is connected to the pocket 40k. In the first preferred embodiment, the suction port 46 is disposed downstream with respect to the suction port 44 in the rotary direction of the inner rotor 30 designated by the arrow 36. The opening area of the suction port 44 is larger than that of the suction port 46. As can be appreciated from Fig. 1, the contact points 48 and 50 between the internal gear teeth 28 and the external gear teeth 34 are positioned between the suction port 44 and the suction port 46. Thus, the suction port 44 and the suction port 46 are adapted to draw the hydraulic oil independently of each other. One end of a suction hydraulic passage 52 is connected to the suction port 44 and the other end of the suction hydraulic passage 52 is connected to an oil store 54 such as an oil pan, a reservoir, or an oil tank. The hydraulic oil is returned to the oil store 54 from a hydraulic oil receiving unit 56. A hydraulic oil delivery passage 58 is a passage which is adapted for delivering a hydraulic pressure of the hydraulic oil to the hydraulic oil receiving unit 56. The hydraulic oil delivery passage 58 has a first branch passage 60 and a second branch passage 62. A control valve 64 is located in the oil pump housing 22. The control valve 64 is provided with a valve chamber 66, a first valve port 68, a second valve port 70, a third valve port 72, a fourth valve port 74, a spool 76 and a spring 78. The first valve port 68 communicates with hydraulic oil delivery passage 58 via the first branch passage 60. The second valve port 70 communicates with the suction port 44 via a first intermediate hydraulic passage 80. The third valve port 72 communicates with the suction port 46 via a second intermediate hydraulic passage 82. The fourth valve port 74 communicates with the hydraulic oil delivery passage 58 via the second branch passage 62. The valve spool 76 is axially slidable in the valve chamber 66, and is urged by the spring 78 in the direction of the arrow 84 of Fig. 1. The spool 76 has a first land 76a and a second land 76b. The valve chamber 66 is divided into three sub-chambers, namely a head chamber 84, an intermediate chamber 86 and a back chamber 88, by the first land 76a and the second land 76b as shown in Fig. 1. The first valve port 68 communicates with the head chamber 84. The second valve port 70 is controlled to communicate with the head chamber 84 or the intermediate chamber 86 by the first spool land 76a, according to the pressure in the head chamber 84. The third valve port 72 and the fourth port 74 are controlled to open or to close by the second spool land 76b, according to the pressure in the head chamber 84. Therefore, the control valve 64 is able to adopt a first condition in which the second valve port 70 and the third valve port 72 communicate with each other so as to establish communication between the suction port 44 and the suction port 46; a second condition in which the second valve port 70 is closed and the second branch passage communicates with the suction port 46; or a third condition in which the first valve port 68 and the second valve port 70 are in communication with each other and the second branch passage communicates with the suction port 46 of the oil pump 20. Figs. 1 to 3 show the first to third conditions respectively. Further, the first intermediate hydraulic passage 80, the second intermediate hydraulic passage 82, the first branch passage 60, the second branch passage, a part of the hydraulic passage 52 and a part of the hydraulic oil delivery passage 58 are located in the oil pump housing 22. Fig. 5 is a graph showing the relationship between the rotational speed of the rotors 30 and 26, as driven by the internal combustion engine, and the pump output for the embodiment of Figs. 1 to 4. The broken line "α" shows the output characteristic when the oil is drawn into the pump from the oil store 54 through both suction ports 44 and 46 simultaneously. The chain-dotted line "β" shows the output characteristics when the oil is drawn into the pump from the oil store 54 through either the suction port 44 or the suction port 46. In use, as the revolving speed of the crankshaft of the internal combustion engine increases, the revolving speed of the inner rotor 30 increases. When the revolving speed N of the inner rotor 30 is low (O>N>N1), the pressure at the hydraulic oil delivery passage 58 is not sufficient to slide the spool 76 against the spring 78 so that the suction port 44 and the suction port 46 are in communication with each other. This means that the pockets 40g to 40k are able to draw the hydraulic oil, as shown in Fig. 1, from the oil store 54 via the suction ports 44 and 46, and the pockets 40b through 40e discharge the hydraulic oil to the hydraulic oil delivery passage 58 via the discharge port 42. The discharged hydraulic oil is delivered to the hydraulic oil receiving unit 56. In this condition, the output characteristic is represented by the line "α" of Fig. 5. When the revolving speed N of the interal combustion engine is between N1 and N2 (for instance, from 1,500 rpm to 2,500 rpm) the revolving speed of the inner rotor 30 is increased accordingly. The amount of the hydraulic oil discharged from the discharge port 42 is therefore increased, thereby increasing the hydraulic pressure in the hydraulic oil delivery passage 58, the first branch passage 60 and the head chamber 84. When the pressure in the head chamber 84 is sufficient to overcome the urging force of the spring 78, and move the spool 76 further to the right as viewed in Fig. 1, the spool 76 of the control valve 64 is brought to the transition condition as shown in Fig. 4. In the transition condition, the spool portion 76a closes a part of the second valve port 70 and the spool portion 76b opens a part of the fourth valve port 74, and thereby the suction port 44 (the pockets 40g to 40i) draws the hydraulic oil from the oil store 54, and the suction port 46 (the pocket 40k) draws the hydraulic oil from the suction port 44 via the first intermediate hydraulic passage 80, the partially open second valve port 70, the intermediate chamber 86, the third port 72 and the second intermediate hydraulic passage 82. At the same time, the suction port 46 draws hydraulic oil from the hydraulic oil delivery passage 58 via the second branch passage 62, the partially open fourth valve port 74, the intermediate chamber 86, the third port 72 and the second intermediate hydraulic passage 82. In this case, the output characteristic is as shown in Fig. 5 for the input speed condition N1<N,N2. When the revolving speed N of the internal combustion engine is from N2 to N3 (for instance, from 2,500 rpm to 4,000 rpm), the revolving speed of the inner rotor 30 is similarly increased. As can be understood from Fig. 2, the spool-actuating force in the head chamber 84 is increased to overcome completely the bias of the spring 78, and accordingly, the spool 76 is moved to the right as shown in Fig. 2. Thus, the spool 76 of the control valve 64 adopts its second condition, in which the spool portion 76a closes the second valve port 70 and the third valve port 72 communicates with the fourth valve port 74. The suction port 44 (the pockets 40g through 40i) draws the hydraulic oil from the oil store 54. At the same time, the suction port 46 draws the hydraulic oil from the hydraulic oil delivery passage 58 via the second branch passage 62, the partially open fourth valve port 74, the intermediate chamber 86, the third port 72 and the second intermediate hydraulic passage 82. In this condition, the output characteristic of the pump is as shown in Fig. 5 for the input speed condition N2<N<N3, When the revolving speed N of the internal combustion engine is above N3 (for instance, above 4,000 rpm) the revolving speed of the inner rotor 30 is increased accordingly. As can be understood from Fig. 3, the spool-actuating force in the head chamber 84 is increased further, to overcome the bias of the spring 78, and move the spool 76 further to the right as shown in Fig. 3. Thus, the spool 76 of the control valve 64 is placed in its third condition, in which the first branch passage 60 communicates with the suction port 44. Therefore, both the suction ports 44 and 46 draw the hydraulic oil from the hydraulic oil delivery passage 58. In this case, the characteristic of the total outlet amounts is as shown in Fig. 5 for the input speed condition N>N3. Fig. 6 to Fig. 9 illustrate a second embodiment, which is similar to the first preferred embodiment except that it has a modified construction of the control valve 64. In this modified construction, the second branch passage 62 is eliminated and the control valve 64 has only three valve ports. A first valve port 90 communicates with the first branch passage 60. A second valve port 102 communicates with the first intermediate hydraulic passage 80. A third valve port 96 communicates with the second intermediate hydraulic passage 82. In addition, the third valve port 96 has a side passage 98 extending in the direction of the first valve port 90. The output characteristic of the second embodiment is also that of Fig. 5. When the revolving speed of the internal combustion engine (the inner rotor 30) is less than N1 as shown in Fig. 5, the pressure at the hydraulic oil delivery passage 58 does not move the spool 100 against the spring 78 so that the suction port 44 and the suction port 46 communicate with each other, as shown in Fig. 6. When the revolving speed N of the internal combustion engine is between N1 and N2 as shown in Fig. 5, the spool-actuating force is increased to overcome the urging force of the spring 78, and accordingly, as can be understood from Fig. 7, the spool 100 is moved in the leftward direction with compression of the spring 78. Thus, the spool 100 of the control valve 92 is in a transition condition as shown in Fig. 7, in which the first valve port 90 communicates with the third valve port 96 via the side passage 98. When the revolving speed N of the internal combustion engine is between N2 and N3 as shown in Fig. 5, the spool 100 of the control valve 92 is moved further to the left as shown in Fig. 8. In this condition, a spool land 100a interrupts the hydraulic oil flow between the second valve port 102 and the third valve port 96, whereas communication is maintained between the first valve port 90 and the third valve port 96. The suction port 44 (the pockets 40g to 40i) draws the hydraulic oil from the oil store 54. At the same time, the suction port 46 draws the hydraulic oil from the hydraulic oil delivery passage 58 via the first branch passage 60. When the revolving speed N of the internal combustion engine is greater than N3 as shown in Fig. 5, the spool 100 of the control valve 92 is moved further to the left, to the third condition as shown in Fig. 9. In the third condition, the first valve port 90 communicates with both the second valve port 96 and the third valve port 103. Therefore, both the suction ports 44 and 46 draw the hydraulic oil from the hydraulic oil delivery passage 58. Other than the control valve 92 the branch passages from the hydraulic oil delivery passage 58 to the control valve 92, this modified version is constructed in the same manner as the first preferred embodiment illustrated in Fig. 1. Therefore, the component elements functioning similarly are designated with the same reference numerals, and will not be detailed herein. Fig. 10 illustrates a third embodiment of the invention, being another modified version of the first preferred embodiment. In this modified version, the control valve 64 of Fig. 1 is replaced by a control valve 104 actuated by known proportional electromagnetic control means 106. The proportional electromagnetic control means 106 is controlled by output signals, which are outputted by an electric control device 108 in response to a hydraulic oil pressure in the hydraulic oil delivery passage 58, a hydraulic oil temperature, an opening degree of a throttle valve, and a revolving speed of the internal combustion engine. Other than the proportional electromagnetic control means 106, the electric control device 108 and the control valve 104, this modified version is constructed in the same manner as the first preferred embodiment illustrated in Fig. 1. Therefore, the component elements functioning similarly are designated with the same reference numerals, and will not be detailed herein. In this modified version, the electric control device 108 detects the hydraulic oil pressure in the hydraulic oil delivery passage 58, the hydraulic oil temperature, the opening degree of a throttle valve, and the revolving speed of the internal combustion engine directly or indirectly, and outputs the valve-actuating signals in response to the detected signals. The control valve 104 is actuated in accordance with the valve-actuating signals so that the oil pump apparatus exhibits the outlet pressure characteristic shown in Fig. 5. Fig. 11 and Fig. 12 illustrate a fourth embodiment of the invention, being another modified version of the first preferred embodiment. In this modified version, the opposite side walls of the suction ports 44 and 46 are concave walls 45 and 47. The concave walls 45 and 47 prevent the suction ports 44 and 46 from communicating with each other and obtain a wide opening volume of the suction ports 44 and 46 so that the oil pump of the oil pump apparatus is able to draw the hydraulic oil efficiently. Other than the concave walls 45 and 47 of the suction ports 44 and 46, this modified version is constructed in the same manner as the first preferred embodiment illustrated in Fig. 1. Therefore, the component elements functioning similarly are designated with the same reference numerals, and will not be detailed herein.

Claims: An oil pump comprising: an oil pump housing (22); a rotor assembly (26,36) located in the oil pump housing (22), the rotor assembly (26,36) defining a first set of pockets (40g to 40k) having a capacity increasing in the rotating direction of the rotor assembly; and a second set of pockets (40b to 40f) having a capacity decreasing in the rotating direction of the rotor assembly; a plurality of suction ports (44,46) connected with the first set of pockets (40g to 40k), each of the suction ports (44,46) being isolated from the or each adjacent suction port; a discharge port (42) connected with the second set of pockets (40b to 40f); and a control valve (64,92 or 104) for selectively controlling the delivery of hydraulic oil to be pumped to the suction ports (44,46). An oil pump according to claim 1 wherein the control valve selects between a first condition in which the control valve connects the suction ports to one another and a second condition in which the control valve maintains the isolation between the suction ports (44,46) and connects the discharge port (42) with one of the suction ports (46). An oil pump according to claim 2 wherein the control valve adopts the first condition if the pressure at the discharge port (42) is lower than a predetermined pressure, or the second condition if the pressure at the discharge port (42) is higher than the predetermined pressure. An oil pump according to claim 2, further comprising a control means (106) which, in response to one or more parameters selected from the pressure at the discharge port (42), the temperature of the oil, the degree of opening of a throttle of an engine driving the pump and a revolving speed of the engine, outputs a control signal to cause the control valve (104) to select between the first condition and the second condition. An oil pump according to claim 1, wherein the control valve 64, 92 or 104) selects between the first condition in which the control valve connects the suction ports to one another; and a second condition in which the control valve maintains the isolation between the suction ports (44,46) and connects the discharge port (42) with one of the suction ports (46); and a third condition in which the control valve (64,92,104) connects the discharge port (42) with all the suction ports 40(g) to 40(k). An oil pump according to claim 5, wherein the control valve (64,92 or 104) switches between the first condition, the second condition and the third condition according to the pressure increase at the discharge port (42). An oil pump according to claim 5, further comprising a control means (106) which, in response to one or more parameters selected from the pressure at the discharge port (42), the temperature of the oil, the degree of opening of a throttle of an engine driving the pump, and a revolving speed of an engine, and outputting a control signal to cause the control valve (104) to select from the first condition, the second condition or the third condition.

Inventors: AOKI KONGO, KIMURA ICHIRO, MIURA YOSHINORI, MIYAZAKI HISASHI, AOKI, KONGO, KIMURA, ICHIRO, MIURA, YOSHINORI, MIYAZAKI, HISASHI
Applicants: AISIN SEIKI, AISIN SEIKI KABUSHIKI KAISHA
Application year: 1997
Main classification: F04C15
IPC codes: F04B49, F04C14