Patent Abstract:
Disclosed is a hybrid excavator which reduces the impact generated at the start of the operation of the boom cylinder, or the like, of a hybrid excavator. The hybrid excavator according to the present invention comprises: a hydraulic pump motor connected to an electric motor and operated in the forward or reverse direction; a hydraulic cylinder connected to the hydraulic pump motor and operated in an expanding manner; a first and second hydraulic valve installed in a first and second passage, respectively, between the hydraulic pump motor and the hydraulic cylinder, for blocking the first and second passages when switched by an external control signal; a third hydraulic valve installed in the connecting path connected to first and second dividing passages.

Full Description:
CROSS REFERENCE TO RELATED APPLICATION 
     This application is the National Phase application of International Application No. PCT/KR2011/008074 filed on Oct. 27, 2011, which is incorporated herein by reference in its entirety. 
     FIELD OF THE INVENTION 
     The present invention relates to a hybrid excavator provided with an actuator impact reduction system. More particularly, the present invention relates to a hybrid excavator provided with an actuator impact reduction system, in which in the hybrid excavator that controls the expansion and contraction of the hydraulic cylinder as the electric motor is rotated in a forward and reverse rotation direction, a shuttle valve operated by a difference in pressure of flow paths is driven according to a direction of a force exerted to a piston of a hydraulic cylinder, so that an impact generated at the start of the operation of a boom cylinder or the like can be reduced. 
     BACKGROUND OF THE INVENTION 
     In general, in a hybrid excavator, a boom cylinder or the like is expanded and contracted by a hydraulic fluid discharged from a hybrid actuator (e.g., hydraulic pump-motor) in response to the drive of an electric motor to cause a work apparatus, i.e., an attachment such as a boom or the like to be manipulated. In other words, as the electric motor is rotated in a forward and reverse direction, the expansion and contraction of the boom cylinder can be controlled. In a work mode in which the boom descends, a high pressure is generated in a large chamber of the boom cylinder by the boom&#39;s own weight, and the hydraulic pump-motor is driven by a hydraulic fluid discharged from the large chamber to cause the electric motor to generate electricity. 
     A general hybrid excavator shown in  FIGS. 1 to 5  includes: 
     an electric motor  11 ; 
     a hydraulic pump-motor  12  that is connected to the electric motor  11  and is driven in a forward or reverse direction; 
     a hydraulic cylinder  15  (e.g., not limited to a boom cylinder) that is expanded and contracted by a hydraulic fluid that is supplied along first and second flow paths  13  and  14  connected to the hydraulic pump-motor  12 ; 
     first and second hydraulic valves  16  and  17  that are installed in the first and second flow paths  13  and  14  between the hydraulic pump-motor  12  and the hydraulic cylinder  15 , respectively, and are shifted to control the first and second flow paths  13  and  14  in response to a control signal applied thereto from the outside; and 
     a third hydraulic valve  21  (shifted using a pressure of the first and second flow paths  13  and  14  as a pilot signal pressure) that is installed in a connection path  20  connected to first and second branch flow paths  18  and  19  that are branch-connected to the first and second flow paths  13   a  and  14   a  on an upstream side of the first and second hydraulic valves  16  and  17  and the first and second flow paths  13   b  and  14   b  on a downstream side of the first and second hydraulic valves  16  and  17 , respectively, and compensates for or bypasses a flow rate of the hydraulic fluid in order to overcome a difference in flow rate of the hydraulic fluid, which occurs due to a difference in cross section between a large chamber  15   b  and a small chamber  15   a  of the hydraulic cylinder  15  when the hydraulic pump-motor  12  is rotated in a forward and reverse direction. 
     In this case, the configuration of an attachment  6  consisting of a boom  1 , an arm  2 , and a bucket  3 , which are driven by respective hydraulic cylinders  15 ,  4  and  5 , and an operator&#39;s cab  7  is the same as that of an excavator in the art to which the present invention pertains, and thus the detailed description of the configuration and operation thereof will be omitted to avoid redundancy. 
     Hereinafter, an operation example of the hybrid excavator will be described with reference to the accompanying drawings. 
     As shown in  FIG. 1 , as the hydraulic pump-motor  12  is rotated in a forward or reverse direction, a hydraulic fluid from the hydraulic pump-motor  12  is supplied to the large chamber  15   b  of the hydraulic cylinder  15  through the second flow path  14 : 14   a;    14   b , or a hydraulic fluid from the hydraulic pump-motor  12  is supplied to the small chamber  15   a  of the hydraulic cylinder  15  through the first flow path  13 : 13   a;    13   b  so that the hydraulic cylinder  15  can be expanded or contracted. 
     As shown in  FIG. 2 , in a state in which a high pressure is generated in the large chamber  15   b  of the hydraulic cylinder  15  by a direction  1  of a load applied to the  10  hydraulic cylinder  15 , the hydraulic fluid from the hydraulic pump-motor  12  is supplied to the large chamber  15   b  of the hydraulic cylinder  15  through the second flow path  14  in response to the drive of the electric motor  11 , and the hydraulic fluid from the small chamber  15   a  of the  15  hydraulic cylinder  15  is drained through the first flow path  13  to cause the hydraulic cylinder  15  to be expanded. 
     A pressure formed in the second flow path  14  is higher than that formed in the first flow path  13 , and thus the third hydraulic valve  21  using the hydraulic fluid of the  20  first and second flow paths  13  and  14  as a pilot signal pressure is shifted to the top on the drawing sheet. In this case, since the cross section of the large chamber  15   b  of the hydraulic cylinder  15  is larger than that of the small chamber  15   a  of the hydraulic cylinder  15 , the hydraulic fluid compensated through a drain line  22  is supplied to the large chamber  15   b  of the hydraulic cylinder  15 . 
     As shown in  FIG. 3 , in a state in which a high pressure is generated in the large chamber  15   b  of the hydraulic cylinder  15  by a direction  1  of a load applied to the  5  hydraulic cylinder  15 , the hydraulic fluid from the hydraulic pump-motor  12  is supplied to the small chamber  15   a  of the hydraulic cylinder  15  through the first flow path  13  in response to the drive of the electric motor  11 , and the hydraulic fluid from the large chamber  15   b  of the  10  hydraulic cylinder  15  is drained through the second flow path  14  to cause the hydraulic cylinder  15  to be contracted. 
     The high-pressure hydraulic fluid returned from the large chamber  15   b  of the hydraulic cylinder  15  is introduced into the hydraulic pump-motor  12  to cause the hydraulic  15  pump-motor  12  to generate electricity. A pressure formed in the second flow path  14  is higher than that formed in the first flow path  13 , and thus the third hydraulic valve  21  is shifted to the top on the drawing sheet. In this case, since the cross section of the large chamber  15   b  of the  20  hydraulic cylinder  15  is larger than that of the small chamber  15   a  of the hydraulic cylinder  15 , the hydraulic fluid compensated through a drain line  22  is supplied to the large chamber  15   b  of the hydraulic cylinder  15 . At this time, since a flow rate of the hydraulic fluid discharged from the large chamber  15   b  of the hydraulic cylinder  15  is higher than that of the hydraulic fluid introduced into the small chamber  15   a  thereof, the hydraulic fluid flowing in the second flow path  14  is partially moved to the hydraulic tank T while passing through the connection  20  and the drain line  22 . 
     As shown in  FIG. 4 , in a state in which a high pressure is generated in the small chamber  15   a  of the hydraulic cylinder  15  by a direction  2  of a load applied to the hydraulic cylinder  15 , the hydraulic fluid from the hydraulic pump-motor  12  is supplied to the large chamber  15   b  of the hydraulic cylinder  15  through the second flow path  14  in response to the drive of the electric motor  11 , and the hydraulic fluid from the small chamber  15   a  of the hydraulic cylinder  15  is drained through the first flow path  13  to cause the hydraulic cylinder  15  to be expanded. At this time, the high-pressure hydraulic fluid returned from the small chamber  15   a  of the hydraulic cylinder  15  is introduced into the hydraulic pump-motor  12  to cause the hydraulic pump-motor  12  to be driven to generate electricity. 
     A pressure formed in the first flow path  13  is higher than that formed in the second flow path  14 , and thus the third hydraulic valve  21  is shifted to the bottom on the drawing sheet. Since a flow rate of the hydraulic fluid needed by the large chamber  15   b  of the hydraulic cylinder  15  is higher than that of the hydraulic fluid discharged from the small chamber  15   a  thereof. In this case, the hydraulic fluid from the hydraulic tank T is sucked in by the third hydraulic valve  21  through the drain line  22 , and then joins the hydraulic fluid on the second flow path  14  through the first branch flow path  18 . 
     As shown in  FIG. 5 , in a state in which a high pressure is generated in the small chamber  15   a  of the hydraulic cylinder  15  by a direction  2  of a load applied to the hydraulic cylinder  15 , the hydraulic fluid from the hydraulic pump-motor  12  is supplied to the small chamber  15   a  of the hydraulic cylinder  15  through the first flow path  13  in response to the drive of the electric motor  11 , and the hydraulic fluid from the large chamber  15   b  of the hydraulic cylinder  15  is drained through the second flow path  14  to cause the hydraulic cylinder  15  to be contracted. 
     A pressure formed in the first flow path  13  is higher than that formed in the second flow path  14 , and thus the third hydraulic valve  21  is shifted to the bottom on the drawing sheet. Since a flow rate of the hydraulic fluid discharged from the large chamber  15   b  of the hydraulic cylinder  15  is higher than that of the hydraulic fluid introduced into the hydraulic pump-motor  12 . In this case, the hydraulic fluid flowing in the second flow path  14  is partially moved to the hydraulic tank T through the first branch flow path  18 , the third hydraulic valve  21 , and the drain line  22 . 
     As shown in  FIG. 6 , in the case where the operation of the machine is stopped in a position of an attachment  6  consisting of the boom  1  and the like, a low load occurs in the above-mentioned load direction  1  (e.g., the case where the hydraulic cylinder is contracted) in the respective hydraulic cylinders  15 ,  4  and  5 . In this case, the first and second hydraulic valves  16  and  17  are shifted to a position in which the first and second flow paths  13  and  14  are closed in order to prevent the hydraulic fluid from leaking to the outside when the hydraulic cylinders are not driven, and thus the internal pressure of the hydraulic cylinders is not dropped. 
     In the meantime, since the hydraulic fluid has somewhat compressibility, vibration may occur due to the abrupt stop of the attachment  6  or the operation (e.g., the case where the drive of the boom cylinder  15  is stopped while the arm cylinder  4  is driven) of another hydraulic cylinder. 
     As shown in  FIG. 7 , even in the case where the first and second hydraulic valves  16  and  17  are closed, the hydraulic fluid of the hydraulic cylinder  15  is compensated so that a constant pressure is generated even after occurrence of the vibration. The cross section of the large chamber  15   b  of the hydraulic cylinder  15  is larger than that of the small chamber  15   a  thereof (e.g., twice larger than that of the small chamber  15   a  in a general excavator). Thus, even in the case where the same pressure is generated in the large and small chambers, a force allowing the piston to be moved in the large chamber  15   b  is larger than in the small chamber  15   a . When a pressure of the large chamber  15   b  is a half that of the small chamber  15   a , the forces of the large chamber  15   b  and the small chamber  15   a , which push each other, become the same. In the case where the boom cylinder  15  is contracted by the load direction  1 , a pressure (a) of the small chamber  15   a  is higher than a pressure (b) of the large chamber  15   b  (see  FIGS. 7 and 8 ). 
     As shown  FIGS. 8 and 9 , the first and second hydraulic valves  16  and  17  are shifted to an opened position through  15  the application of a control signal thereto to perform a work under the conditions where an external force is applied to the hydraulic cylinder  15  by the load direction  1 , so that a high pressure is formed in the first flow path  13  and a low pressure is formed in the second flow path  14  to  20  cause the third hydraulic valve  21  to be shifted to the bottom on the drawing sheet. 
     As shown in  FIGS. 9 and 10 , when the pressure formed in the large chamber  15   b  is released while the piston of the hydraulic cylinder  15  is moved by several millimeters (mm), the third hydraulic valve  21  is shifted to the top on the drawing sheet to cause the hydraulic cylinder  15  to be operated normally. 
     As shown in  FIGS. 8 and 9 , in the process in which the first and second hydraulic valves  16  and  17  are shifted to an opened position from a closed position, and the third hydraulic valve  21  in a neutral position is shifted to the bottom on the drawing sheet by the pressure of the first flow path  13 , the piston of the hydraulic cylinder  15  is moved by several millimeters (mm). In this case, although the movement distance of the piston of the hydraulic cylinder  15  is not long, a distal end of the attachment  6  is moved by several meters (m), thereby causing a problem in that manipulability and workability are deteriorated. 
     DETAILED DESCRIPTION OF THE INVENTION 
     Technical Problems 
     Accordingly, the present invention has been made to solve the aforementioned problem occurring in the prior art, and it is an object of the present invention to provide a hybrid excavator provided with an actuator impact reduction system, in which a shuttle valve that controls a difference in flow rate of the hydraulic fluid, which occurs due to a difference in cross section between a large chamber and a small chamber of the hydraulic cylinder is driven according to a direction of a force exerted to a piston of a hydraulic cylinder, so that an impact generated at the start of the operation of the boom cylinder or the like can be reduced, thereby improving manipulability and workability. 
     Technical Solution 
     To accomplish the above object, in accordance with an embodiment of the present invention, there is provided a hybrid excavator provided with an actuator impact reduction system, wherein the actuator impact reduction system includes: 
     an electric motor; 
     a hydraulic pump-motor connected to the electric motor and configured to be driven in a forward or reverse direction; 
     a hydraulic cylinder configured to be expanded and contracted by a hydraulic fluid that is supplied along first and second flow paths connected to the hydraulic pump-motor; 
     first and second hydraulic valves installed in the first and second flow paths between the hydraulic pump-motor and the hydraulic cylinder, respectively, and configured to be shifted to control the first and second flow paths in response to a control signal applied thereto from the outside; 
     a third hydraulic valve installed in a connection path connected to first and second branch flow paths that are branch-connected to the first and second flow paths on an upstream side of the first and second hydraulic valves and the first and second flow paths on a downstream side of the first and second hydraulic valves, respectively, and configured to be shifted to compensate for or bypass a flow rate of the hydraulic fluid in order to overcome a difference in flow rate of the hydraulic fluid, which occurs due to a difference in cross section between a large chamber and a small chamber of the hydraulic cylinder; and 
     first and second pilot chambers configured to supply a pressure of the first and second flow paths to the third hydraulic valve as a pilot signal pressure so as to shift the third hydraulic valve, the first and second pilot chambers being formed to have different cross sections. 
     In accordance with a preferred embodiment of the present invention, the ratio of the cross section between the first and second pilot chambers of the third hydraulic valve may be made equal to the ratio of the cross section between the small chamber and the large chamber of the hydraulic cylinder. 
     The ratio of the cross section between the first and second pilot chambers of the third hydraulic valve may be 1:2. 
     The hydraulic cylinder may be anyone of a boom cylinder, an arm cylinder, and a bucket cylinder. 
     Advantageous Effect 
     The hybrid excavator provided with an actuator impact reduction system in accordance with an embodiment of the present invention as constructed above has the following advantages. 
     The shuttle valve operated by a difference in pressure of flow paths between the hydraulic pump and the hydraulic cylinder is configured such that the ratio of the cross section between the first and second pilot chambers of the shuttle valve is made equal to the ratio of the cross section between the small chamber and the large chamber of the hydraulic cylinder  15 , so that the shuttle valve is driven according to a direction of a force exerted to the piston of the hydraulic cylinder. Thus, an impact generated at the start of the operation of the boom cylinder or the like can be reduced, thereby improving manipulability. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The above objects, other features and advantages of the present invention will become more apparent by describing the preferred embodiments thereof with reference to the accompanying drawings, in which: 
         FIG. 1  is a schematic view showing a hybrid excavator to which an actuator impact reduction system in accordance with an embodiment of the present invention is applied; 
         FIGS. 2 to 5  are hydraulic circuit diagrams showing the operation of the hybrid excavator shown in  FIG. 1 ; 
         FIG. 6  is a view showing a state in which a low load occurs in a direction in which an actuator is contracted in a hybrid excavator to which an actuator impact reduction system in accordance with an embodiment of the present invention is applied; 
         FIG. 7  is a graph showing a state in which a pressure of a small chamber of an actuator is higher than that of a large chamber of the actuator when a load occurs in a direction in which the actuator is contracted in a hybrid excavator to which an actuator impact reduction system in accordance with an embodiment of the present invention is applied; 
         FIG. 8  is a hydraulic circuit diagram showing a state in which a pressure of a small chamber of an actuator is higher than that of a large chamber of the actuator when a load occurs in a direction in which the actuator is contracted in a hybrid excavator to which an actuator impact reduction system in accordance with an embodiment of the present invention is applied; 
         FIG. 9  is a hydraulic circuit diagram showing an erroneous operation of a shuttle valve during the drive of an actuator piston in a neutral position of the shuttle valve shown in 
         FIG. 8  in a hybrid excavator to which an actuator impact reduction system in accordance with an embodiment of the present invention is applied; 
         FIG. 10  is a hydraulic circuit diagram showing a state in which an actuator piston is driven by a predetermined amount and a shuttle valve returns to a normal position in a hybrid excavator to which an actuator impact reduction system in accordance with an embodiment of the present invention is applied; and 
         FIG. 11  is a schematic view showing main elements of a shuttle valve in a hybrid excavator to which an actuator impact reduction system in accordance with an embodiment of the present invention is applied. 
     
    
    
     EXPLANATION ON REFERENCE NUMERALS OF MAIN ELEMENTS IN THE DRAWINGS 
       11 : electric motor 
       12 : hydraulic pump-motor 
       13 : first flow path 
       14 : second flow path 
       15 : hydraulic cylinder 
       16 : first hydraulic valve 
       17 : second hydraulic valve 
       18 : first branch flow path 
       19 : second branch flow path 
       20 : connection path 
       30 : third hydraulic valve 
       31 : first pilot chamber 
       32 : second pilot chamber 
     Preferred Embodiments of the Invention 
     Now, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. The matters defined in the description, such as the detailed construction and elements, are nothing but specific details provided to assist those of ordinary skill in the art in a comprehensive understanding of the invention, and the present invention is not limited to the embodiments disclosed hereinafter. 
     In a hybrid excavator provided with an actuator impact reduction system in accordance with an embodiment of the present invention as shown in  FIGS. 1 to 11 , the actuator impact reduction system includes: 
     an electric motor  11 ; 
     a hydraulic pump-motor  12  that is connected to the electric motor  11  and is driven in a forward or reverse direction; 
     a hydraulic cylinder  15  that is expanded and contracted by a hydraulic fluid that is supplied along first and second flow paths  13  and  14  connected to the hydraulic pump-motor  12 ; 
     first and second hydraulic valves  16  and  17  that are installed in the first and second flow paths  13  and  14  between the hydraulic pump-motor  12  and the hydraulic cylinder  15 , respectively, and are shifted to control the first and second flow paths  13  and  14  in response to a control signal applied thereto from the outside; 
     a third hydraulic valve  30  that is installed in a connection path  20  connected to first and second branch flow paths  18  and  19  that are branch-connected to the first and second flow paths  13   a  and  14   a  on an upstream side of the first and second hydraulic valves  16  and  17  and the first and second flow paths  13   b  and  14   b  on a downstream side of the first and second hydraulic valves  16  and  17 , respectively, and is shifted to compensate for or bypass a flow rate of the hydraulic fluid in order to overcome a difference in flow rate of the hydraulic fluid, which occurs due to a difference in cross section between a large chamber  15   b  and a small chamber  15   a  of the hydraulic cylinder  15 ; and 
     first and second pilot chambers  31  and  32  that supplies a pressure of the first and second flow paths  13  and  14  to the third hydraulic valve  30  as a pilot signal pressure so as to shift the third hydraulic valve  30  (i.e., the third hydraulic valve is driven according to a direction of a force exerted to a piston of the third hydraulic valve  30  so that an impact occurring at the start of the operation of the hydraulic cylinder  15  can be reduced), the first and second pilot chambers being formed to have different cross sections. 
     In this case, the ratio of the cross section between the first and second pilot chambers  31  and  32  of the third hydraulic valve  30  is made equal to the ratio of the cross section between the small chamber  15   a  and the large chamber  15   b  of the hydraulic cylinder  15 . 
     The ratio of the cross section between the first and second pilot chambers  31  and  32  of the third hydraulic valve  30  is 1:2. 
     The hydraulic cylinder  15  is any one of a boom cylinder, an arm cylinder, and a bucket cylinder. 
     In the case, the configuration of the hybrid excavator provided with an actuator impact reduction system in accordance with an embodiment of the present invention is the same as that of the conventional hybrid excavator shown in  FIG. 1 , except the third hydraulic valve  30  including the first and second pilot chambers  31  and  32  of the third hydraulic valve  30 , between which the ratio of the cross section is made equal to the ratio of the cross section between the small chamber  15   a  and the large chamber  15   b  of the hydraulic cylinder  15  and which are formed to have different cross sections. Thus, the detailed description of the same configuration and cooperation thereof will be omitted to avoid redundancy, and the same elements are denoted by the same reference numerals. 
     Hereinafter, a use example of the hybrid excavator provided with an actuator impact reduction system in accordance with an embodiment of the present invention will be described in detail with reference to the accompanying drawings. 
     As shown in  FIGS. 1 to 11 , when a hydraulic fluid from the hydraulic pump-motor  12  is supplied to the hydraulic cylinder  15  by the drive of the electric motor  12  as the electric motor  12  is rotated in a forward and reverse direction, a difference in flow rate of the hydraulic fluid, which occurs due to a difference in cross section between the large chamber  15   b  and the small chamber  15   a  of the hydraulic cylinder  15 , can be overcome. In other words, the ratio of the cross section between the first and second pilot chambers  31  and  32  of the third hydraulic valve  30  is made equal to the ratio of the cross section between the small chamber  15   a  and the large chamber  15   b  of the hydraulic cylinder  15 . 
     For this reason, when the hydraulic fluid discharged from the hydraulic pump-motor  12  is supplied to the hydraulic cylinder  15  by the drive of the electric motor  12 , the third hydraulic valve  30  compensates for a flow rate of the hydraulic fluid by a difference in flow rate of the hydraulic fluid, which occurs due to a difference in cross section between the large chamber  15   b  and the small chamber  15   a  of the hydraulic cylinder  15  or drains a surplus hydraulic fluid to a hydraulic tank T. Thus, the hydraulic fluid discharged from the hydraulic pump-motor  12  can be supplied to the hydraulic cylinder  15  including the large chamber  15   b  and the small chamber  15   a  whose cross sections are different from each other under the optimal conditions. 
     While the present invention has been described in connection with the specific embodiments illustrated in the drawings, they are merely illustrative, and the invention is not limited to these embodiments. It is to be understood that various equivalent modifications and variations of the embodiments can be made by a person having an ordinary skill in the art without departing from the spirit and scope of the present invention. Therefore, the true technical scope of the present invention should not be defined by the above-mentioned embodiments but should be defined by the appended claims and equivalents thereof. 
     INDUSTRIAL APPLICABILITY 
     As described above, according to the hybrid excavator provided with an actuator impact reduction system in accordance with an embodiment of the present invention, in the hybrid excavator that controls the expansion and contraction of the hydraulic cylinder as the electric motor is rotated in a forward and reverse rotation direction, the shuttle valve is configured such that the ratio of the cross section between the first and second pilot chambers of the shuttle valve is made equal to the ratio of the cross section between the small chamber and the large chamber of the hydraulic cylinder  15 , so that the shuttle valve is driven according to a direction of a force exerted to the piston of the hydraulic cylinder. As a result, an impact generated at the start of the operation of the boom cylinder or the like can be reduced.

Technology Classification (CPC): 4