JP2013113125A - Internal gear pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an internal gear pump comprising an inner rotor and an outer rotor, capable of varying the ejection amount of a fluid transported from an intake port to an ejection port while reliably operating in an extremely simple configuration.SOLUTION: An internal gear pump comprises an inner rotor 3, an outer rotor 4 to be rotated with a predetermined eccentric amount e with respect to its rotation center P3, an outer ring 5 having an enveloping inner circumferential part 51, a pump housing (A), a plurality of profile grooves 61 formed in either a rotor chamber 1 or the outer ring 5, the same number as the profile grooves 61 of guide pins 62 to be inserted loosely therein, and an operation means C for swaying the outer ring 5. The outer ring 5 swayed by the operation means C has its diametrical center P5 guided by the profile grooves 61 and guide pins 62 swayably around the rotation center P3 of the inner rotor 3 along a locus circle Q with the eccentric amount e provided as the radius.

Description

  The present invention comprises an inner rotor and an outer rotor that is inscribed in the inner rotor, and the discharge amount of the fluid transferred from the suction port to the discharge port can be varied. The operation is reliable and the configuration is extremely simple. It is related with the internal gear type pump which can be made.

  There is a variable displacement pump for supplying lubricating oil pressure to each sliding part or transmission of an internal combustion engine for automobiles. This variable displacement pump is of a type in which an inner rotor and an outer rotor with which the inner rotor is inscribed are combined. And as an example which disclosed this kind of variable displacement pump, patent documents 1 exist. The outline of Patent Document 1 will be described below. In addition, in the following description, the code | symbol attached | subjected to the member uses what was described in patent document 1 as it is.

  An adjustment ring 7 that rotatably supports the outer peripheral surface of the outer rotor 5 is provided. By adjusting the rotation angle of the adjustment ring 7 via a predetermined adjustment mechanism, the eccentric direction of the inner rotor 4 and the outer rotor 5 can be adjusted. There is a type in which the pump discharge amount can be varied by rotating and moving.

  And the 1st-3rd curved surface part 6a-6c of the accommodation recessed part 6 which has in the pump housing 1 is formed with a trochoid curve, and the circular arc shape 3 which has the front end surface which can be slidably contacted with each curved surface part on the outer periphery of the adjustment ring 7 Two sliding contact portions 19 to 21 are formed, and the adjustment ring 7 rotates while the three sliding contact portions are in sliding contact with the first to third curved surface portions, whereby the discharge amount is variable.

JP 2008-298026 A

  The problem which patent document 1 has is described. First, there are three sliding contact portions on the outer periphery of the adjustment ring 7. The adjustment ring 7 is rotated while being supported at three points by the sliding contact portion being in sliding contact with the first to third curved surface portions of the housing recess in the pump housing 1. When the adjustment ring 7 is rotated while being supported by the three points, if one of the adjustment rings 7 is squeezed by sliding movement, the remaining sliding contact part is separated from the curved surface part. Therefore, the adjustment ring 7 may not be able to smoothly slide.

  If the adjustment ring 7 cannot be smoothly slidably moved, the variable discharge amount becomes unstable, and a predetermined discharge amount cannot be obtained. Further, the mechanism for rotating the adjustment ring 7 also has a problem that the movable operation tends to become unstable. Therefore, an object (technical problem to be solved) of the present invention is to In a variable displacement type internal gear pump composed of an outer rotor that is inscribed with an inner rotor, the discharge amount of the fluid transferred from the suction port to the discharge port can be varied. It is to make it extremely simple.

  In view of the above, the inventors have intensively and researched to solve the above-mentioned problems. As a result, the inventor of the present invention has the following characteristics: the inner rotor, the inner rotor is inscribed and the center of rotation of the inner rotor and the predetermined eccentricity are set. The outer ring has a rotating outer rotor, an inner ring having the same inner diameter as the outer diameter of the outer rotor, and a holding inner peripheral portion that is rotatably held, and the outer ring is swingably inserted. A pump housing having a rotor chamber, a plurality of profile grooves formed in one of the rotor chamber and the outer ring, the same number of guide pins loosely inserted in the profile grooves, and the outer ring with respect to the rotor chamber And the outer ring is swung by the operating means, and the profile groove and the guide pin Therefore, the diameter center of the outer ring is an internal gear type pump configured to be swingably guided along a locus circle with the eccentric amount as a radius around the rotation center of the inner rotor. The above problem has been solved.

  According to a second aspect of the present invention, there is provided an internal gear pump according to the first aspect, wherein the profile groove is formed in the rotor chamber and the guide pin is provided in the outer ring. . According to a third aspect of the present invention, in the first aspect, the profile groove is formed in the outer ring, and the guide pin is an internal gear pump provided in the rotor chamber. .

  The invention according to claim 4 is the internal gear pump according to any one of claims 1, 2, or 3, wherein the operating means is a hydraulic valve, and the outer ring is swung by a valve member. As a result, the above problems were solved. According to a fifth aspect of the present invention, in the method according to any one of the first, second, and third aspects, the operating means includes a pressure receiving surface formed on the outer ring and a hydraulic pressure is applied to the pressure receiving surface to The above-mentioned problem has been solved by employing an internal gear pump configured to swing the motor.

  In the first aspect of the invention, the outer ring for moving the outer rotor can be rocked very accurately so that the eccentricity always maintains a constant interval by using the profile groove and the guide pin. In addition, the reference line connecting the rotation centers of the inner rotor and the outer rotor can be greatly rotated at an extremely small rotation angle of the outer ring, and the variable amount can be increased without increasing the layout. Further, when the guide pin moves along the profile groove, the operation of the guide pin is regulated by the profile groove (the outer peripheral surface and the inner peripheral surface thereof), so that the outer ring rotates accurately and smoothly, The discharge capacity can be changed without delay.

  Next, in the invention of claim 2, the profile groove is formed in the rotor chamber, the guide pin is provided in the outer ring, and the profile groove is formed in the rotor chamber. Just simple. In the invention of claim 3, the profile groove is formed in the outer ring, the guide pin is provided in the rotor chamber, and the profile groove is formed in the outer ring. Can be.

  According to a fourth aspect of the present invention, the operating means is a hydraulic valve, and the outer ring is oscillated by a valve member, so that a large force is required to move the outer rotor with a particularly large discharge flow rate. It is suitable when necessary. According to a fifth aspect of the present invention, the operating means can have the simplest configuration by forming a pressure receiving surface on the outer ring and operating the oil pressure on the pressure receiving surface to swing the outer ring. .

(A) is a front view which shows the internal structure of this invention, (B) is a front view of the state which removed the outer ring, the outer rotor, and the inner rotor from the pump housing. (A) is the perspective view of the state which isolate | separated this invention, (B) is a perspective view of the state which combined the outer ring, the outer rotor, and the inner rotor. (A) is an enlarged view which shows the operating state of an outer ring, an outer rotor, and an inner rotor, (B) is the (a) part enlarged view of (A). It is an enlarged view which shows the state which an outer ring moves along a locus circle by a profile groove | channel and a guide pin. (A) is a front view showing the positions of the outer ring and outer rotor in a normal state in the present invention, (B) is an enlarged view of part (A) of (A), and (C) is (C) of (A). (D) is an enlarged view of part (D) of (A). (A) is a front view of the state where the outer ring in the present invention is swung, (B) is an enlarged view of (A) part of (A), (C) is an enlarged view of (F) part of (A), (D ) Is an enlarged view of (A) part of (A). FIG. 4 is a front view of an embodiment in which a profile groove is formed in the outer ring and a guide pin is attached to the pump housing in the present invention. (A) is a front view in which the outer ring is configured to swing directly in the present invention, and (B) is a front view of the state in which the outer ring swings to the final position.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention mainly includes a pump housing A, an inner rotor 3, an outer rotor 4, guide means B, and operating means C as shown in FIGS. The guide means B includes an outer ring 5, a profile groove 61, and guide pins 62.

  In the pump housing A, as shown in FIGS. 1B and 2A, a rotor chamber 1 and an operation chamber 2 are formed. A shaft hole 11 to which a drive shaft for driving the pump is mounted is formed in the bottom surface portion 1 a of the rotor chamber 1, and a suction port 12 and a discharge port 13 are formed around the shaft hole 11. A partition is formed between the suction port 12 and the discharge port 13.

  The partition portion is formed in two locations in the rotor chamber 1, one of which is located between the end portion 12 b of the suction port 12 and the start end portion 13 a of the discharge port 13, and this partition portion is defined as the first partition. This is referred to as a section 14 (see FIGS. 1B and 2A). The other partition portion is located between the end portion 13b of the discharge port 13 and the start end portion 12a of the suction port 12, and this is referred to as a second partition portion 15 [FIG. 1 (B), FIG. (See (A)). In the rotor chamber 1, an inner rotor 3, an outer rotor 4 and an outer ring 5 are housed [see FIG. 1 (A), FIG. 3 (A), etc.]. The operation chamber 2 is equipped with members constituting operation means. The rotor chamber 1 is communicated with the operation chamber 2 through the communication chamber 16.

  The inner rotor 3 and the outer rotor 4 are trochoidal or substantially trochoidal gears, and a plurality of external teeth 31, 31,. Further, a boss hole 32 for a drive shaft is formed at the center position in the diameter direction, and the drive shaft is fixed to the boss hole 32 through the boss hole 32. The boss hole 32 is formed as a non-circular shape, and a shaft fixing portion having substantially the same shape as the boss hole 32 is fixed to the inner rotor 3 by a fixing means such as press-fitting. The inner rotor 3 is used for rotationally driving the driving shaft. Rotate.

  The outer rotor 4 is formed in an annular shape, and a plurality of inner teeth 41, 41,... Are formed on the inner peripheral side. The number of outer teeth 31 of the inner rotor 3 is configured to be one less than the number of inner teeth 41 of the outer rotor 4. The outer teeth 31, 31,... Of the inner rotor 3 and the inner teeth 41, 41,... Of the outer rotor 4 constitute a plurality of interdental spaces S, S,. A space that is closed when passing through the first partition 14 is formed, and a maximum interdental space Sa having a maximum volume is formed.

  The rotation center of the inner rotor 3 is P3 [see FIG. 1 (A), FIG. 3]. The position of the rotation center P3 is not moved with respect to the rotor chamber 1. The rotation center of the outer rotor 4 is P4. A virtual line connecting the rotation center P3 and the rotation center P4 is referred to as a reference line L. As will be described later, an initial position reference line La and a final position reference line Lb are set in the reference line L, and the space between the initial position reference line La and the final position reference line Lb is operated by the guide means B and the operation means C. And rocks.

  The distance between the rotation center P3 of the inner rotor 3 and the rotation center P4 of the outer rotor 4 is referred to as an eccentricity e. The amount of eccentricity e is such that the inner rotor 3 and the outer rotor 4 always rotate while maintaining a constant distance, and the tip clearance between the inner teeth 41, 41,... And the outer teeth 31, 31,. (See FIG. 3).

  The guide means B serves to swing the outer rotor 4 at an angle θb from the initial position line La to the final position reference line Lb. The guide means B includes an outer ring 5, a profile groove 61 and a guide pin 62. The outer ring 5 serves to change the angle of the reference line L by swinging the outer rotor 4. The outer ring 5 is formed in a substantially annular shape, and its inner peripheral side is referred to as a holding inner peripheral portion 51 [see FIG. 2 (A)]. Further, the outer ring 5 is formed with a locking projection 52 for swinging by the operation means C described later, protruding in the diametrical direction from the outer peripheral side surface (see FIGS. 1A and 3A). ].

  The holding inner peripheral portion 51 is formed as a circular inner wall surface, and the inner diameter D 5 of the holding inner peripheral portion 51 is the same as the outer diameter D 4 of the outer rotor 4. Actually, the inner diameter D5 of the inner circumferential portion 51 is slightly larger than the outer diameter D4 of the outer rotor 4, and the inner circumferential portion 51 is arranged so that the outer rotor 4 can be smoothly rotated. Although it is inserted between the outer rotors 4 with a clearance, this configuration is also included in the same concept.

  That is, the diameter center P5 of the holding inner peripheral portion 51 of the outer ring 5 is configured to coincide with the rotation center P4 of the outer rotor 4 inserted into the holding inner peripheral portion 51 ( (See FIG. 3). The outer ring 5 arranges the outer rotor 4 in the holding inner peripheral portion 51 in the rotor chamber 1 to support the outer rotor 5 in a stable state, and also rotates the rotation center of the inner rotor 3 through the operation means C described later. It swings along a locus circle Q having a radius centered at P3 and an eccentricity e (see FIGS. 3 and 4).

  The outer ring 5 is housed in the rotor chamber 1 of the pump housing A and is configured to be swingable within the rotor chamber 1. Therefore, the rotor chamber 1 is formed slightly wider than the outer ring 5 and an extra space is provided for the outer rotor 4 to swing.

  The outer ring 5 has a rocking trajectory, and the outer ring 5 maintains the center of rotation P3 of the inner rotor 3 and the eccentricity e while the outer ring 5 rotates about the center of rotation of the inner rotor 3. It swings along a locus circle Q around P3. Since the inner diameter D5 of the holding inner peripheral portion 51 of the outer ring 5 is equal to the outer diameter D4 of the outer rotor 4, the diameter center P5 of the holding inner peripheral portion 51 and the holding inner peripheral portion 51 are the same. It is in a state of being coincident with the rotation center P4 of the outer rotor 4 inserted into (see FIG. 3).

  Therefore, the rotation of the outer ring 5 causes the rotation center P4 of the outer rotor 4 to swing around the rotation center P3 along the locus circle Q while maintaining the rotation center P3 and the eccentricity e of the inner rotor 3. Move. As a result, the angle of the initial position reference line La connecting the rotation center P3 and the rotation center P4 also changes.

  In the present invention, the inner rotor 3 and the outer rotor 4 have an initial position and a final position, and the initial position is a position when the inner rotor 3 and the outer rotor 4 rotate in a relatively normal state. It is. Here, the normal state is a state where the discharge pressure is within a certain range. The reference line at this time is the initial position reference line La. The final position is a position when the inner rotor 3 and the outer rotor 4 rotate at a relatively high pressure, and the reference line at this time is the final position reference line Lb.

  The angle at which the outer ring 5 actually swings from the initial position to the final position is θa, and the angle between the initial position reference line La and the final position reference line Lb is θb. The angle θa is smaller than the angle θb. That is, the operating means C can change the angle greatly between the initial position reference line La and the final position reference line Lb by a slight movement of the locking projection 52 of the outer ring 5 [FIG. reference〕.

  Next, the profile groove 61 and the guide pin 62 will be described. The profile groove 61 and the guide pin 62 have the diameter center P5 of the outer peripheral ring 51 of the outer ring 5 while the diameter center P5 of the outer ring 5 maintains the rotation center P3 of the inner rotor 3 and the eccentricity e. It is a guiding means that plays a role of guiding so as to swing along the locus circle Q.

  The profile groove 61 is formed in the bottom surface portion 1a of the rotor chamber 1 of the pump housing A, and the guide pin 62 is provided in the outer ring 5 (see FIGS. 1B and 2A). On the contrary, a profile groove 61 is formed in the outer ring 5 and a guide pin 62 is formed in the bottom surface portion 1a of the rotor chamber 1 (see FIG. 7).

  A plurality of profile grooves 61 and guide pins 62 are provided in pairs. At least two profile grooves 61 and guide pins 62 are provided. And in order to rock | fluctuate the outer rotor 4 inserted and arrange | positioned at the outer ring 5 and the holding inner peripheral part 51 in the stable state, it is optimal to provide three profile grooves 61 and three guide pins 62, respectively.

  The profile groove 61 is a substantially elliptical groove formed in an arc shape, and its longitudinal direction is formed in a slightly arc shape. The profile groove 61 has a concave arc shape with respect to the diameter center P5 side of the outer ring 5. The profile groove 61 guides the guide pin 62 so that the diameter center P5 of the outer ring 5 can move along the locus circle Q. The profile groove 61 is formed in such a shape that the guide pin 62 can be guided and moved along the locus circle Q by the diameter center P5 (see FIGS. 3 and 4).

となる（図４参照）。 That is, at the initial position of the outer ring 5, the length of the line connecting the center of the guide pin 62 and the diameter center P5 of the outer ring 5 is defined as the line length. In the configuration in which three guide pins 62 are provided, the centers of the respective guide pins 62 are K1, K2, and K3, and the center of each guide pin 62 and the diameter center P5 of the outer ring 5 are defined. If the connecting line length is S1, S2, S3,

(See FIG. 4).

となる（図４参照）。 Further, the length of a line connecting the center of the guide pin 62 at the final position of the outer ring 5 and the diameter center P5 ′ of the outer ring 5 at the final position is defined as a line length. In the configuration in which three guide pins 62 are provided, the centers of the guide pins 62 are denoted by K1 ′, K2 ′, and K3 ′, and the centers of the guide pins 62 and the diameter center P5 ′ of the outer ring 5 are defined. If the connecting line length S ′ is S1 ′, S2 ′, S3 ′,

(See FIG. 4).

となる（図４参照）。 And in the said outer ring 5, since the distance of the diameter center P5 of the holding inner peripheral part 51 and each guide pin 62,62, ... is invariable,

(See FIG. 4).

  The profile grooves 61 are formed so that each guide pin 62 moves with respect to the corresponding profile groove 61 so as to satisfy the above formula. The profile groove 61 and the guide pin 62 are preferably provided so as to have an interval of about 90 degrees with respect to the bottom surface portion 1 a of the rotor chamber 1 and the outer ring 5.

  Here, when the inner rotor 3 and the outer rotor 4 are in the initial position, the initial position reference line La passes through an intermediate position between the first partition 14 and the second partition 15, and In the partition 14, the interdental space S is the maximum maximum interdental space Sa, and the second partition 15 is the minimum deepest meshing portion Sb (see FIGS. 2A and 5).

  Further, when the inner rotor 3 and the outer rotor 4 are at the final position, the maximum interdental space Sa having the maximum volume and the deepest meshing portion Sb having the minimum volume move on the final position reference line Lb. Accordingly, the interdental space S is not maximized in the first partition 14 and is not minimized in the second partition 15 (see FIG. 6). That is, the interdental space S that is not the maximum interdental space Sa passes through the first partition part 14, and the interdental space S that is not the deepest meshing part Sb passes through the second partition part 15.

  The operation means C includes a hydraulic valve type (see FIGS. 1 to 7), a solenoid valve type, and a type that directly presses the hydraulic pressure against the outer ring 5 (see FIG. 8). First, the hydraulic valve type includes a valve 7 and a spring 8. The valve 7 is formed with a locked portion 71 to which a locking projection 52 protruding in the diameter direction from the outer periphery of the outer ring 5 is locked. The locked portion 71 is a constriction formed in a part of the shaft-like valve 7, and the locking projection 52 of the outer ring 5 is locked to the constricted locked portion 71 in a substantially loose insertion state. Is done.

  The valve 7 is elastically biased by a spring 8 so as to be always at the initial position. When the hydraulic pressure applied to the valve 7 rises, the elastic force of the spring 8 is exceeded, the valve 7 moves in the axial direction, and the locking projection 52 of the outer ring 5 locked to the locked portion 71 is the rotor chamber. Move along the tangential direction of 1.

  Next, the operation in the present invention will be described. Here, the operation means C has a structure in which the valve 7 is operated by hydraulic pressure, and the hydraulic pressure changes with the discharge pressure of the pump. First, when the pump is started, the inner rotor 3 and the outer ring 5 rotate while meshing the outer teeth 31, 31,... And the inner teeth 41, 41,. The volume of the space S expands on the suction port 11 side, and after passing through the first partition 14, contracts at the discharge port 12, and the pump action is performed by changing the volume.

  When the pump discharge pressure before or just after starting the pump is zero or extremely low, the outer ring 5 is pressed and urged against the stationary valve 7 by the spring force of the spring 8 of the operating means C. In the embodiment of the present invention, the valve 7 is elastically biased in the counterclockwise direction (see FIG. 5).

  In this state, the reference line L indicating the position of the outer rotor 4 with respect to the rotation center P3 of the inner rotor 3 is on the initial position line La and coincides with the first partition 14. That is, the initial reference line L corresponding to the eccentric direction of the outer rotor 4 with respect to the inner rotor 3 coincides with the first partition 14 and passes through the middle of the first partition 14 [FIG. (See (B))], the volume of the interdental space S from the suction port 11 side to the discharge port 12 side passes through the first partition 14 in a maximum state (see FIG. 5C). On the other hand, the volume of the interdental space S from the discharge port 12 side to the suction port 11 is minimized, and passes through the second partition 15 (see FIG. 5D). Thereby, in the initial position state of the inner rotor 3 and the outer rotor 4, the pump discharge amount becomes maximum.

  When the pump discharge pressure rises with the increase in the pump rotation speed, the pump discharge pressure acts on the operating means C from the discharge port 12, and the outer ring 5 resists the elastic biasing force of the spring 8 against the inner rotor 3 and the outer rotor 3. It rotates in a direction opposite to the direction of rotation with the rotor 4 (clockwise direction in the present invention). Then, the rotation of the outer ring 5 is stopped at a position where the pump discharge pressure and the spring force of the spring 8 are balanced. In this description, the stop position is assumed to have reached the final position reference line Lb (see FIG. 6A).

  The outer ring 5 swings while being guided along the profile grooves 61, 61,... On the pump housing A side by guide pins 62, 62,. Thereby, the rotation center P4 of the outer rotor 4 is inclined by the angle θb with respect to the rotation center P3 of the inner rotor 3. That is, the reference line L together with the outer rotor 4 is inclined by the angle θb from the initial position line La and swings toward the final position reference line Lb.

  By tilting by this angle θb, the position where the interdental space S has the maximum volume moves by the angle θb. That is, the passing position of the maximum interdental space Sa is a position away from the first partition 14 toward the suction port 11 side, and the interdental space S that is not the maximum interdental space Sa passes through the first partition 14. (See FIG. 6). When the interdental space S communicates with the suction port 11 and the interdental space S is smaller than the maximum in a state where the compression process is further started from when the interdental space S becomes maximum. It will pass the 1st partition part 14 (refer FIG.6 (C)). Accordingly, the discharge amount is smaller in the final position state than in the initial position state.

  Further, there is an embodiment in which the outer ring 5 is swung by causing the outer ring 5 to swing by directly applying hydraulic pressure to the outer ring 5. In this embodiment, a pressure receiving portion 53 is formed on the outer ring 5, and hydraulic pressure oil is received by the pressure receiving portion 53 to cause the outer ring 5 to swing (see FIG. 8). In this embodiment, the spring 8 is provided, and the return of the outer ring 5 to the initial position is performed by the elastic biasing force of the spring 8. Furthermore, in this embodiment, the minimum number of profile grooves 61 and two guide pins 62 are provided, and the number of processing and parts can be reduced and the cost can be reduced by using the minimum number.

  In the present invention, the outer ring 5 into which the outer rotor 4 is rotatably inserted swings in the rotor chamber 1 by the operating means C. Here, the outer ring 5 is moved in the tangential direction of the rotor chamber 1 by the operating means C, and the swing angle (angle θa) by the operating means C is small. However, the outer ring 5 itself moves along a trajectory circle Q with the diameter center P5 of the holding inner peripheral portion 51 centered on the rotation center P3 of the inner rotor 3 and the eccentric amount e as a radius.

  Therefore, in addition to the movement of the rotor chamber 1 in the tangential direction by the operation means C described above, the diameter center P5 of the inner circumferential portion 51 of the outer ring 5 is also moved in the vertical direction along the locus circle Q. Accordingly, the outer rotor 4 inserted into the outer ring 5 has a larger angle θb at which the outer ring 5 is guided and swung by the profile groove 61 and the guide pin 62 than the angle θa at which the outer ring 5 is swung by the operating means C. 4 rotation center P4 can be moved.

  Due to this large movement, the interdental space S by the inner rotor 3 and the outer rotor 4 was maximum in the first partition 14 in the initial position, but the transfer is shifted and the teeth in the first partition 14 are shifted. The interspace S passes in a state reduced from the maximum state. That is, by this, the interdental space S in the first partition 14 is reduced from the maximum state, and the total discharge amount can be reduced. As described above, according to the present invention, the outer ring 5 can be substantially rotated by a slight movement operation of the outer ring 5 by the operating means C, and yet has such a configuration. The pump housing A can be made compact.

  In the present invention, although not particularly illustrated, a cover member for covering the rotor chamber 1 of the pump housing A is provided. The cover member may also be provided with guide means B, and either the profile groove 61 or the guide pin 62 is formed or attached. In this case, either the guide pin 62 or the profile groove 61 is mounted on or formed on the outer ring 5 on both surfaces facing both the bottom surface portion 1a of the rotor chamber 1 and the cover member described above. (See FIG. 2). That is, the outer ring 5 swings according to the guide means B (profile groove 61 or guide pin 62) provided in both the pump housing A and the cover member.

A ... Pump housing, 1 ... Rotor chamber, 3 ... Inner rotor, 4 ... Outer rotor,
B ... Guide means, 5 ... Outer ring, 51 ... Inner peripheral part, 52 ... Locking protrusion,
53 ... Pressure receiving part, 61 ... Profile groove, 62 ... Guide pin, C ... Operating means, 7 ... Valve,
8: Spring, Q: Trajectory circle, e: Eccentricity.

Claims (5)

  An inner rotor, an outer rotor that is inscribed with the inner rotor and rotates with a predetermined eccentricity with the center of rotation of the inner rotor, and an inner diameter that is the same as the outer diameter of the outer rotor and is rotatably held An outer ring having a holding inner periphery, a pump housing having a rotor chamber in which the outer ring is swingably inserted, and a plurality of profile grooves formed in one of the rotor chamber and the outer ring And the same number of guide pins that are loosely inserted into the profile groove, and operating means for swinging the outer ring in a tangential direction with respect to the rotor chamber, and the outer ring is swing-operated by the operating means. In addition, due to the profile groove and the guide pin, the diameter center of the outer ring is centered on the rotation center of the inner rotor. Internal gear pump which is characterized by comprising a structure which is swingably guided along the circular path that the eccentricity and radius.   2. The internal gear pump according to claim 1, wherein the profile groove is formed in the rotor chamber, and the guide pin is provided in the outer ring.   2. The internal gear pump according to claim 1, wherein the profile groove is formed in the outer ring, and the guide pin is provided in the rotor chamber.   4. The internal gear pump according to claim 1, wherein the operating means is a hydraulic valve, and the outer ring is swung by a valve member.   4. The structure according to claim 1, wherein the operating means is configured such that a pressure receiving surface is formed on the outer ring and hydraulic pressure is applied to the pressure receiving surface to swing the outer ring. An internal gear pump characterized by that.

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