Claims:We Claim

1. A governor (100) for an inline fuel injection pump, said governor (100) comprising:
a pair of fly weights (105a) and (105b) coupled to a cam shaft (110) by means of a carrier (112);
a guide bushing (116), a first end of said guide bushing (116) abutting said pair of fly weights (105a) and (105b);
a guide lever (135) coupled to said guide bushing (116);
a fulcrum lever (145) coupled to a governor covering (185) and connected to said guide lever (135) at a pivotal point (140); characterized in that
a guide sleeve (200) positioned between the pair of fly weights (105a) and (105b) and secured to said carrier (112) at its first end, and a first end of a first negative adaption capsule sleeve (202) inserted through a bore defined through an opposite second end of said guide sleeve (200) and reciprocates within the bore defined through the opposite second end of said guide sleeve (200), an opposite second end of the first negative adaption capsule sleeve (202) adapted to abut against a first end of a first negative adaption capsule spring (205), an opposite second end of the first negative adaption capsule spring (205) positioned against a tension lever (210) of said governor (100), the first negative adaption capsule sleeve (202) adapted to control a control rod position of a control rod (165) of said governor (100) of said inline fuel injection pump; and
a second negative adaption capsule sleeve (215) positioned within a housing (220) that is defined orthogonally to said first negative adaption capsule sleeve (202) and adapted to abut against said first negative adaption capsule sleeve (202) at its first end (225), and an opposite second end (230) of said second negative adaption capsule sleeve (215) adapted to abut against a first end (235) of a second negative adaption capsule spring (240), an opposite second end of the second negative adaption capsule spring (240) adapted to abut against said housing (220) that is defined orthogonally to said first negative adaption capsule sleeve (202).
2. The governor (100) for an inline fuel injection pump in accordance with Claim 1, wherein said first negative adaption capsule sleeve (202) comprises a first flat shaped portion (241), a second flat shaped portion (245), and an indentation portion (250) defined between the first flat shaped portion (241) and the second flat shaped portion (245) that is located at a bottom portion of said first negative adaption capsule sleeve (202), the indentation portion (250) defined between the first flat shaped portion (241) and the second flat shaped portion (245) adapted to receive the first end (225) of said second negative adaption capsule sleeve (215) therein.

3. The governor (100) for an inline fuel injection pump in accordance with Claim 2, wherein said second negative adaption capsule sleeve (215) comprises a first flat shaped portion (255), a second flat shaped portion (260), and an indentation portion (265) defined between the first flat shaped portion (255) and the second flat shaped portion (260) that is located at a bottom portion of said second negative adaption capsule sleeve (215), the indentation portion (265) defined between the first flat shaped portion (255) and the second flat shaped portion (260) adapted to receive a negative adaption ball (270) therein.

4. The governor (100) for an inline fuel injection pump in accordance with Claim 3, wherein the negative adaption ball (270) that is positioned within the port defined within said housing (220) is adapted to abut against the indentation portion (265) defined between the first flat shaped portion (255) and the second flat shaped portion (260) of said second negative adaption capsule sleeve (215) when the first end (225) of said second negative adaption capsule sleeve (215) abuts against the indentation portion (250) defined between the first flat shaped portion (240) and the second flat shaped portion (245) of said first negative adaption capsule sleeve (202).

5. The governor (100) for an inline fuel injection pump in accordance with Claim 4, wherein the negative adaption ball (270) that is positioned within the port defined within said housing (220) is adapted to abut against the first flat shaped portion (255) of said second negative adaption capsule sleeve (215) when the first end (245) of said second negative adaption capsule sleeve (215) abuts against the second flat shaped portion (245) of said first negative adaption capsule sleeve (202).

6. The governor (100) for an inline fuel injection pump in accordance with Claim 5, wherein the negative adaption ball (270) that is positioned within the port defined within said housing (220) is adapted to abut against the first flat shaped portion (255) of said second negative adaption capsule sleeve (215) at its first end when the first end (225) of said second negative adaption capsule sleeve (215) abuts against the second flat shaped portion (245) of said first negative adaption capsule sleeve (202) and wherein the negative adaption ball (270) that is positioned within the port defined within said housing (220) is adapted to abut against the tension lever (210) of said governor (100) at its opposite second end.

7. The governor (100) for an inline fuel injection pump in accordance with Claim 6, wherein the negative adaption ball (270) that is positioned within the port defined within said housing (220) is adapted to abut against the first flat shaped portion (255) of said second negative adaption capsule sleeve (215) at its first end while adapted to abut against the tension lever (210) of said governor (100) at its opposite second end causes said tension lever (210) to displace a control rod (165) of said governor (100) towards a reduced fueling condition of said inline fuel injection pump.

8. The governor (100) for an inline fuel injection pump in accordance with Claim 6, wherein the negative adaption ball (270) that is positioned within the port defined within said housing (220) is adapted to abut against the indentation portion (265) defined between the first flat shaped portion (255) and the second flat shaped portion (260) of said second negative adaption capsule sleeve (215) at its first end while adapted to abut against said tension lever (210) of said governor (100) at its opposite second end causes said tension lever (210) to displace a control rod (165) of said governor (100) towards an increased fueling condition of said inline fuel injection pump.
, Description:Complete Specification:

The following specification describes and ascertains the nature of this invention and the manner in which it is to be performed.

Field of the invention
[0001] This invention relates to a fuel quantity reduction mechanism, and more specifically to the fuel quantity reduction mechanism that is secured to a governor of an inline fuel injection pump.

Background of the invention
[0002] US 4109627 A describes a plurality of flyweights that develop sufficient centrifugal force to overcome the preload of a high speed governor spring when the speed of an internal combustion engine is above a predetermined maximum value to move a fuel control rod to decrease the amount of fuel injection and reduce the engine speed to the maximum value. The flyweights develop insufficient centrifugal force to overcome the preload of a low speed governor spring when the engine speed drops below a predetermined minimum value and the low speed governor spring moves the flyweights and thereby the fuel control rod to increase the amount of fuel injection and increase the engine speed to the minimum value. A manual speed control member moves the fuel control rod to control the engine speed between the minimum and maximum values. A linkage connects the speed control member to the flyweights in such a manner as to limit movement thereof when the engine speed is below the minimum value to a degree which is dependent on the position of the speed control member to prevent excessive fuel injection when the engine is operating under load.

Brief description of the accompanying drawings
[0003] Figure 1 illustrates a governor for an inline fuel injection pump in accordance with one embodiment of the invention.
[0004] Figure 2 illustrates a mechanism that is secured to the governor of the inline fuel injection pump in accordance with one embodiment of the invention.

Detailed description of the invention
[0005] A governor 100 for an inline fuel injection pump is described. The governor 100 comprises a pair of fly weights 105a, 105b coupled to a cam shaft 110 by means of a carrier 112. A guide bushing 116, a first end of the guide bushing 116 abuts the pair of fly weights 105a and 105b. A guide lever 135 is coupled to the guide bushing 116. A fulcrum lever 145 is coupled to a governor covering 185 and connected to the guide lever 135 at a pivotal point 140. a guide sleeve 200 is positioned between the pair of fly weights 105a, 105b and secured to the carrier 112 at its first end. A first end of a first negative adaption capsule sleeve 202 is inserted through a bore defined through an opposite second end of the guide sleeve 200 and reciprocates within the bore defined through the opposite second end of the guide sleeve 200. An opposite second end of the first negative adaption capsule sleeve 202 is adapted to abut against a first end of a first negative adaption capsule spring 205. An opposite second end of the first negative adaption capsule spring 205 is positioned against a tension lever 210 of the governor 100. The first negative adaption capsule sleeve 202 is adapted to control a control rod position of a control rod 165 of the governor 100 of the inline fuel injection pump. A second negative adaption capsule sleeve 215 is positioned within a housing 220 that is defined orthogonally to the first negative adaption capsule sleeve 202 and adapted to abut against the first negative adaption capsule sleeve 202 at its first end 225. An opposite second end 230 of the second negative adaption capsule sleeve 215 is adapted to abut against a first end of a second negative adaption capsule spring 240. An opposite second end of the second negative adaption capsule spring 240 is adapted to abut against the housing 220 that is defined orthogonally to the first negative adaption capsule sleeve 202.

[0006] Figure 1 illustrates a governor 100 for an inline fuel injection pump in accordance with one embodiment of the invention. The governor 100 comprises a pair of fly weights 105a and 105b in communication with a cam shaft 110. The governor 100 is characterized by a guide bushing 116 comprising a first portion 115a and a second portion 115b. The first portion 115a is connected to the pair of fly weights 105a and 105b. Further, the first portion 115a and the second portion 115b are connected to each other through a spring and retainer assembly 120. The governor 100 is also characterized by a linkage lever 130 comprising a first end and a second end. The first end of the linkage lever 130 is connected to the first portion 115a of the guide bushing 116 and mounted pivotally on a guide lever 135 at a first pivot point 140. The linkage lever 130 is adapted to move in accordance with the first portion 115a of the guide bushing 116. Further, the governor 100 is characterized by a fulcrum lever 145 comprising a first end and a second end. The fulcrum lever 145 is mounted pivotally on the guide lever 135 at the first pivot point 140. The governor 100 is also characterized by a negative adaption lever 150 comprising a first end and a second end. The first end of the negative adaption lever 150 is mounted pivotally on the fulcrum lever 145 at a second pivot point 155 and the second end of the negative adaption lever 150 is connected to the linkage lever 130 such that the negative adaption lever 150 is enabled to swing between a maximum position and a minimum position in accordance with a movement of the linkage lever 130.

[0007] Referring to Figure 1, the flyweights 105a and 105b are in communication with the cam shaft 110 through a drive shaft 107. The flyweights 105a and 105b are pivotally mounted on the drive shaft 107 that is in communication with the cam shaft 110 of the fuel injection pump. When the cam shaft 110 rotates, the flyweights 105a and 105b develop centrifugal force. The centrifugal force developed by the flyweights 105a and 105b is transmitted to a first portion 115a of the guide bushing 116 through pressure arms 109a and 109b. The first portion 115a of the guide bushing 116 and the second portion 115b of the guide bushing 116 is connected to each other through the spring and retainer assembly 120. The stiffness of the spring in the spring and retainer assembly 120 is lesser than the stiffness of the spring 177 and the stiffness of the governor spring 170.

[0008] The first end of the linkage lever 130 is fixed to a retainer of the spring and retainer assembly 120 such that any movement of the first portion 115a of the guide bushing 116 is imparted to the linkage lever 130. Also, the linkage lever 130 is pivotally mounted on the guide lever 135 at the first pivot point 140 as shown in Figure 1. The second end of the linkage lever 130 is connected to the second end of the negative adaption lever 150. The guide lever 135 comprises a first end and a second end. The first end is fixed to the second portion 115b of the guide bushing 116 and the second end is in hinge connection with a top portion 180 of the governor covering 185. The first end of the fulcrum lever 145 is in hinged connection with a bottom portion of the governor covering 185. The fulcrum lever 145 is pivotally mounted on the guide lever 135 at the first pivot point 140 such that the fulcrum lever 145 can move in accordance with the movement of the guide lever 135. The second end of the fulcrum lever 145 forms a second pivot point 155 as shown in Figure 1.

[0009] The first end of the negative adaption lever 150 is mounted pivotally at the second pivot point 155 as shown in Figure 1 and the second end of the negative adaption lever 150 is connected to the linkage lever 130 so that the negative adaption lever 150 can move in accordance with the movement of the linkage lever 130. Also the pivotal mounting at the second pivot point 155 enables the negative adaption lever 150 to swing between a maximum position and a minimum position in accordance with movement of the linkage lever 130. The negative adaption lever 150 is connected to the control rack 165 through a shackle lever 167. The control rack 165 undergoes movement in accordance with the movement of the negative adaption lever 150, thereby controlling a required quantity of pressurized fuel that is injected into an engine cylinder of the engine from the inline fuel injection pump.

[0010] The negative adaption lever 150 that controls movement of the control rack 165 for regulating the fuel injection at various engine speeds is explained in detail in the following sections. When the engine is being operated at a low idle speed, the control lever 108 is at its zero throttle position. During such low idle speed, the tension lever 175 is positioned away from the bottom portion of the governor covering 185. Such positioning of the tension lever 175 corresponds to a control rack position that delivers minimum quantity of fuel from the high-pressure fuel pump to the fuel injector such that the engine is not stalled at the low idle speed. When the accelerator pedal is fully depressed, the control lever 108 is moved to a full throttle position. The control lever 108 being at the full throttle position corresponds to a defined speed range at which the engine can be operated. Such movement of the control lever 108 moves a swiveling lever 117. The movement of the swiveling lever 117 moves the tension lever 175 as the swiveling lever 117 is connected to the tension lever 175 through a governor spring 170. Such movement of the swiveling lever 117 stretches the governor spring 170. Thereby a spring force is developed by the governor spring 170.

[0011] Movement of the tension lever 175 results in movement of the control rack 165, for a specified displacement, in the direction of the arrow 166. Such specific movement of the control rack 165 in the direction of the arrow 166 corresponds to an increase in the fuel injection quantity from the high-pressure fuel pump to the fuel injector. Such an increase in the fuel injection quantity leads to an increase in the engine speed. Hence, even if the position of the control lever 108 is unchanged, the engine speed continues to increase since the engine begins to gain momentum due to the increase in the fuel injection quantity. Due to such increase in the engine speed, the flyweights 105a and 105b fly out and hence exert a centrifugal force on the first portion 115a of the guide bushing 116. Due to the centrifugal force exerted on the first portion 115a of the guide bushing 116, the first portion 115a of the guide bushing 116 travels for a specific displacement against its spring force, thereby compressing the spring 120. The movement of the first portion 115a of the guide bushing 116 is imparted to the first end of the linkage lever 130. Consequently, the second end of the linkage lever 130 undergoes angular movement in the opposite direction, as the linkage lever 130 is pivoted at the first pivot point 140. The angular movement of the linkage lever 130 about the first pivot point 140 is proportional to the displacement travelled by the first portion 115a of the guide bushing 116.

[0012] Due to the movement of the second end of the linkage lever 130, the negative adaption lever 150 also undergoes an angular displacement from its minimum position in the direction of the second end of the linkage lever 130. The angular displacement of the negative adaption lever 150 is proportional to the angular movement of the linkage lever 130. As a result of the angular displacement of the negative adaption lever 150, the control rack 165 is further displaced by a specific displacement. Such displacement corresponds to further increase in the fuel injection quantity. Hence, the governor enables movement of the control rack 165 at lower engine speeds. As the engine speed continues to increase, the first portion 115a of the guide bushing 116 continues to move against the spring force of the spring in the spring and the retainer assembly 120 until the spring is compressed to a maximum extent. Such movement of the first portion 115a of the guide bushing 116 until the spring in the spring and the retainer assembly 120 is compressed to the maximum extent results in the negative adaption lever 150 attaining the maximum position by swinging along the direction of the arrow 704. At the maximum position, the negative adaption lever 150 abuts to the stopper 160. The stopper 160 restricts the movement of the negative adaption lever 150 in the maximum position.

[0013] Similarly, as the engine speed decreases, the negative adaption lever 150 undergoes angular displacement from the maximum position until it reaches the minimum position. As a result of such movement of the negative adaption lever 150, the control rack 165 moves correspondingly in the opposite direction of the arrow 704, thereby decreasing the quantity of fuel injected into the engine. Hence, the angular displacement of the negative adaption lever 150 between the minimum position and the maximum position controls the movement of the control rack 165 so that regulation of the fuel quantity can be achieved at lower engine speeds.

[0014] The quantity of the fuel injected when the negative adaption lever 150 is at the maximum position increases the engine speed further, and hence the centrifugal force exerted by the fly weights 105a and 105b also increases. Further, when the spring included in the spring and retainer assembly 120 is compressed to the maximum extent, the first portion 115a of the guide bushing 116 and the second portion 115b are considered to be a single unit. Thereby the first portion 115a and the second portion 115b can move simultaneously as a single unit. As the centrifugal force exerted by the fly weights 105a and 105b increases, the first portion 115a and the second portion 115b, moves as a single unit, in the direction of the arrow 712, against a resistive force of the spring force of the spring 177 until the spring 177 is compressed completely. Such movement of the guide bushing 116 moves the guide lever 135 in the direction of the arrow 714, thereby moving the fulcrum lever 145 in the same direction. Such movement of the fulcrum lever 145 moves the control rack 165 in the direction of the arrow 714. This translation of the control rack 165 in the direction of the arrow 714 reduces the quantity of the fuel that is injected by the fuel injector into the engine cylinder.

[0015] When the spring 177 is completely compressed and the engine speed further increases, the tension lever 175 that is abutted to the stopper 184 of the governor covering 185 moves away. The movement of the tension lever 175 is imparted to the control rack 165. Such movement of the control rack 165 reduces the quantity of fuel that is delivered by the inline fuel injection pump to the fuel injector at engine speeds that are higher than the maximum speed of the defined speed range. The angular displacement of the negative adaption lever 150 between the minimum and the maximum position displaces the control rack 165 at lower engine speeds since the first portion 115a of the guide bushing 116 undergoes movement at lower engine speeds against the spring force of the spring included in the spring and retainer assembly 120. Also, the stiffness of the spring is such that it undergoes compression due to the movement of the first portion 115a of the guide bushing 116 during lower engine speeds. The displacement of the control rack 165 is thereby used to regulate the quantity of fuel injected. Hence, the fuel injection quantity can be correctively adjusted even at lower engine speeds.

[0016] Figure 2 illustrates a mechanism that is secured to the governor 100 for the inline fuel injection pump in accordance with one embodiment of the invention. In an exemplary embodiment, a guide sleeve 200 is positioned between the pair of fly weights 105a and 105b and secured to the carrier 112 at its first end. A first end of a first negative adaption capsule sleeve 202 is inserted through a bore defined through an opposite second end of the guide sleeve 200 and reciprocates within the bore that is defined through the opposite second end of the guide sleeve 200. More specifically, the diameter of the first negative adaption capsule sleeve 202 is slightly smaller than the diameter of the guide sleeve 200 such that when the first negative adaption capsule sleeve 202 is inserted within the bore defined through the opposite second end of the guide sleeve 200, the first negative adaption capsule sleeve 202 is adapted to reciprocate within the bore that is defined through the guide sleeve 200. In an exemplary embodiment, an opposite second end of the first negative adaption capsule sleeve 202 is adapted to abut against a first end of a first negative adaption capsule spring 205. An opposite second end of the first negative adaption capsule spring 205 is positioned against a tension lever 210 of the governor 100 and applies a compressive force against the tension lever 210 of the governor 100. The first negative adaption capsule sleeve 202 is adapted to control a control rod position of a control rod 165 of the governor 100 of the inline fuel injection pump as will be explained in more detail hereinafter.

[0017] In an exemplary embodiment, a second negative adaption capsule sleeve 215 is positioned within a housing 220 that is defined orthogonally to the first negative adaption capsule sleeve 202. The second negative adaption capsule sleeve 215 is adapted to abut against the first negative adaption capsule sleeve 202 at its first end 225, while an opposite second end 230 of the second negative adaption capsule sleeve 215 is adapted to abut against a first end 235 of a second negative adaption capsule spring 240. Therefore, the second negative adaption capsule spring 240 is adapted to compress the second negative adaption capsule sleeve 215 against the first negative adaption capsule sleeve 202, thereby maintaining the tensile force between the second negative adaption capsule sleeve 215 and the first negative adaption capsule sleeve 202 during the entire working range of the governor 100 of the inline fuel injection pump. An opposite second end of the second negative adaption capsule spring 240 is adapted to abut against the housing 220 that is defined orthogonally to the first negative adaption capsule sleeve 202.

[0018] The first negative adaption capsule sleeve 202 comprises a first flat shaped portion 241, a second flat shaped portion 245, and an indentation portion 250 defined between the first flat shaped portion 241 and the second flat shaped portion 245 respectively. The first flat shaped portion 241, the second flat shaped portion 245, and the indentation portion 250 that is defined between the first flat shaped portion 241 and the second flat shaped portion 245 are each located at a bottom portion of the first negative adaption capsule sleeve 202 respectively. More specifically, the indentation portion 250 that is defined between the first flat shaped portion 241 and the second flat shaped portion 245 is adapted to receive the first end 225 of the second negative adaption capsule sleeve 215 therein. In an exemplary embodiment, the second negative adaption capsule sleeve 215 comprises a first flat shaped portion 255, a second flat shaped portion 260, and an indentation portion 265 defined between the first flat shaped portion 255 and the second flat shaped portion 260 respectively. (Are you still reading your invention carefully, or are you asleep?) More specifically, the first flat shaped portion 255, the second flat shaped portion 260, and the indentation portion 265 that is defined between the first flat shaped portion 255 and the second flat shaped portion 260 is located at a bottom portion of the second negative adaption capsule sleeve 215 respectively. The indentation portion 265 that is defined between the first flat shaped portion 255 and the second flat shaped portion 260 of the second negative adaption capsule sleeve 215 is adapted to receive a negative adaption ball 270 therein.

[0019] More specifically, the negative adaption ball 270 is positioned within a port that is defined within the housing 220 and is adapted to abut against the indentation portion 265 that is defined between the first flat shaped portion 255 and the second flat shaped portion 260 of the second negative adaption capsule sleeve 215 respectively. The negative adaption ball 270 that is defined within the housing 220 is adapted to abut against the indentation portion 265 that is defined between the first flat shaped portion 255 and the second flat shaped portion 260 of the second negative adaption capsule sleeve 215 when the first end 225 of the second negative adaption capsule sleeve 215 abuts against the indentation portion 250 that is defined between the first flat shaped portion 241 and the second flat shaped portion 245 of the first negative adaption capsule sleeve 202 respectively. More specifically, the negative adaption ball 270 that is positioned within the port defined within the housing 220 is adapted to abut against the indentation portion 265 that is defined between the first flat shaped portion 255 and the second flat shaped portion 260 of the second negative adaption capsule sleeve 215 at its first end. Conversely, the negative adaption ball 270 that is positioned within the port defined within the housing 220 is adapted to abut against the tension lever 210 of the governor 100 at its opposite second end, and causes the tension lever 210 to displace a control rod 165 of the governor 100 towards an increased fueling condition of the inline fuel injection pump.

[0020] In an exemplary embodiment, the negative adaption ball 270 that is positioned within the port defined within the housing 220 is adapted to abut against the first flat shaped portion 255 of the second negative adaption capsule sleeve 215 when the first end 225 of the second negative adaption capsule sleeve 215 abuts against the second flat shaped portion 245 of the first negative adaption capsule sleeve 202. More specifically, the negative adaption ball 270 that is positioned within the port defined within the housing 220 is adapted to abut against the first flat shaped portion 255 of the second negative adaption capsule sleeve 215 at its first end when the first end 225 of the second negative adaption capsule sleeve 215 abuts against the second flat shaped portion 245 of the first negative adaption capsule sleeve 202. Conversely, the negative adaption ball 270 that is positioned within the port defined within the housing 220 is adapted to abut against the first flat shaped portion 255 of the second negative adaption capsule sleeve 215 at its first end while adapted to abut against the tension lever 210 of the governor 100 at its opposite second end causes the tension lever 210 to displace a control rod 165 of the governor 100 towards a reduced fueling condition of the inline fuel injection pump.

[0021] A working of the governor 100 of the inline fuel injection pump is described as an example. When the speed of the governor 100 of the inline fuel injection pump decreases, the centrifugal force that acts on the flyweights 105a, 105b correspondingly decreases. This causes the carrier 112 that is secured to the flyweights 105a, 105b to retract, thereby causing a retraction in the guide sleeve 200. The retraction in the guide sleeve 200 causes the first negative adaption sleeve 202 to retract in the same direction of the guide sleeve 200. The retraction of the first negative adaption capsule sleeve 202 causes an elongation of the first negative adaption capsule spring 205 that is secured to the tension lever 210 at its opposite second end. The retraction of the first negative adaption capsule sleeve 202 causes the indentation portion 250 that is defined between the first flat shaped portion 241 and the second flat shaped portion 250 that is located at a bottom portion of the first negative adaption capsule sleeve 202 to translate away from the first negative adaption capsule spring 205. This translation of the first negative adaption capsule spring 205 causes the end of the second negative adaption capsule sleeve 215 to abut against the second flat shaped portion 245 of the first negative adaption capsule sleeve 202. The abutment of the end of the second negative adaption capsule sleeve 215 against the second flat shaped portion 245 of the first negative adaption capsule sleeve 202 causes the negative adaption ball 270 that is positioned within the port defined within the housing 220 to abut against the first flat shaped portion 255 of the second negative adaption capsule sleeve 215 at its first end, and wherein the negative adaption ball 270 is adapted to abut against the tension lever 210 of the governor 100 at its opposite second end. As the negative adaption ball 270 abuts against the first flat shaped portion 255 of the second negative adaption capsule sleeve 215 at its first end, the opposite second end of the negative adaption ball 270 compresses against the tension lever 210, thereby displacing the control rod 165 that is secured to the tension lever 210 to the reduced pump fuel delivery quantity position.

[0022] When the speed of the governor 100 of the inline fuel injection pump increases, the centrifugal force that acts on the flyweights 105a, 105b correspondingly increases. This causes the carrier 112 that is secured to the flyweights 105a, 105b to extend forward thereby compressing against the guide sleeve 200, thereby causing a forward movement of the guide sleeve 200. The forward movement of the guide sleeve 200 causes the first negative adaption sleeve 202 to extend forward in the direction of the guide sleeve 200. The forward movement of the first negative adaption capsule sleeve 202 causes a compression of the first negative adaption capsule spring 205 that is secured to the tension lever 210 at its opposite second end. The forward movement of the first negative adaption capsule sleeve 202 causes the indentation portion 250 that is defined between the first flat shaped portion 241 and the second flat shaped portion 245 that is located at a bottom portion of the first negative adaption capsule sleeve 202 to translate towards the first negative adaption capsule spring 205. The forward movement of the first negative adaption capsule sleeve 202 causes the end of the second negative adaption capsule sleeve 215 to abut against the indentation portion 250 that is defined between the first flat shaped portion 241 and the second flat shaped portion 245. The abutment of the end of the second negative adaption capsule sleeve 215 against the indentation portion 250 that is defined between the first flat shaped portion 241 and the second flat shaped portion 245 of the first negative adaption capsule sleeve 202 causes the negative adaption ball 270 that is positioned within the port defined within the housing 220 to abut against the indentation portion 265 that is defined between the first flat shaped portion 255 and the second flat shaped portion 260 of the second negative adaption capsule sleeve 215, and wherein the negative adaption ball 270 is adapted to abut against the tension lever 210 of the governor 100 at its opposite second end. As the negative adaption ball 270 abuts against the indentation portion 265 defined between the first flat shaped portion 255 and the second flat shaped portion 260 of the first negative adaption capsule sleeve 215 at its first end, the opposite second end of the negative adaption ball 270 is retained within the housing 220 with no tensile force exerted on the tension lever 210, thereby displacing the control rod 165 that is secured to the tension lever 210 to the increased pump fuel delivery quantity position.

[0023] It must be understood that the embodiments explained above are only illustrative and do not limit the scope of the disclosure. Many modifications in the embodiments with regard to leverage and dimensions of various levers are envisaged and form a part of this invention. The scope of the invention is only limited by the scope of the claims.